CN114576228B - Flow amplifying valve and steering hydraulic control system thereof - Google Patents
Flow amplifying valve and steering hydraulic control system thereof Download PDFInfo
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- CN114576228B CN114576228B CN202210484550.XA CN202210484550A CN114576228B CN 114576228 B CN114576228 B CN 114576228B CN 202210484550 A CN202210484550 A CN 202210484550A CN 114576228 B CN114576228 B CN 114576228B
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- steering
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D5/00—Power-assisted or power-driven steering
- B62D5/06—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle
- B62D5/08—Power-assisted or power-driven steering fluid, i.e. using a pressurised fluid for most or all the force required for steering a vehicle characterised by type of steering valve used
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a flow amplifying valve and a steering hydraulic control system thereof, comprising: the valve comprises a valve body, an amplifying valve rod, a control spring, a main oil duct, a first oil duct, a second oil duct, a first reversing valve and a second reversing valve. The valve rod of the amplifying valve is horizontally arranged in a valve cavity of the valve body, and a first oil port and a second oil port are respectively formed at two ends of the valve body by two ports of the valve cavity. The control spring is sleeved on the outer wall of the valve rod of the amplification valve. The main oil duct is positioned in the valve body, and two ends of the main oil duct are respectively communicated with two ends of the valve cavity. Two ends of the first oil duct are respectively communicated with the right part of the main oil duct and the right part of the valve cavity, and two ends of the second oil duct are respectively communicated with the left part of the main oil duct and the left part of the valve cavity. The first reversing valve is located in the first oil duct, the second reversing valve is located in the second oil duct, and the two reversing valves are respectively communicated with the third oil duct and the fourth oil duct. The flow amplifying valve provided by the invention overcomes the problem that the existing flow amplifying steering hydraulic system causes the whole vehicle to shake left and right when the steering wheel rotates unevenly and stops rotating.
Description
Technical Field
The invention relates to the technical field of loaders, in particular to a flow amplifying valve and a steering hydraulic control system thereof.
Background
The information disclosed in this background of the invention is only for the purpose of increasing an understanding of the general background of the invention and is not necessarily to be construed as an admission or any form of suggestion that this information forms the prior art that is already known to a person skilled in the art.
At present, the loaders of 6 tons and above basically use a BZZ3 steering gear and a ZLF25E type flow amplifying valve, pilot control oil of the ZLF25E type flow amplifying valve comes from the BZZ3 steering gear, when a steering wheel rotates, the BZZ3 steering gear outputs the control oil, a valve core of the ZLF25E type flow amplifying valve is opened under the action of the control oil, and oil from a steering pump is switched to a steering cylinder through the valve port of the flow amplifying valve to realize the steering of the whole loader; when the steering wheel is suddenly stopped, the BZZ3 steering gear can quickly return to the neutral position, and the valve core of the ZLF25E flow amplifying valve can also quickly return to the neutral position under the action of a control spring, so that the valve port of the flow amplifying valve is closed, and the steering of the whole machine is stopped. However, the existing flow amplifying steering hydraulic system has the shaking problem when steering, namely: the problem that the whole vehicle shakes leftwards and rightwards when the steering wheel is not uniform in rotating speed and stops rotating is solved, particularly, when the steering wheel stops rotating suddenly, the whole vehicle shakes leftwards and rightwards seriously, driving comfort and safety are affected, and the service lives of related parts are shortened.
Disclosure of Invention
Aiming at the problems, the invention provides a flow amplifying valve and a steering hydraulic control system thereof, wherein the flow amplifying valve is matched with a load sensing steering gear, and the problem that the existing flow amplifying steering hydraulic system causes the left and right shaking of the whole vehicle when the steering wheel is not uniform in rotating speed and stops rotating is effectively solved. In order to achieve the above object, the technical solution of the present invention is as follows.
In a first aspect, a flow amplifying valve is disclosed, comprising: the valve comprises a valve body, an amplifying valve rod, a control spring, a main oil duct, a first oil duct, a second oil duct, a first reversing valve and a second reversing valve. Wherein: the amplifying valve rod is horizontally arranged in a valve cavity of the valve body, and a first oil port and a second oil port are respectively formed at two ends of the valve body through two ports of the valve cavity. The control spring is sleeved on the outer wall of one end of the amplification valve rod, so that the amplification valve rod is reset conveniently. The main oil duct is positioned in the valve body, and two ends of the main oil duct are respectively communicated with two ends of the valve cavity, so that hydraulic oil can conveniently circulate in the valve body. The upper end of the first oil duct is communicated with the right part of the main oil duct, the lower end of the first oil duct is communicated with the right part of the valve cavity, the upper end of the second oil duct is communicated with the left part of the main oil duct, and the lower end of the second oil duct is communicated with the left part of the valve cavity. The first reversing valve is arranged in the first oil duct, the second reversing valve is arranged in the second oil duct, the first reversing valve is communicated with a third oil duct arranged in the valve body, and the second reversing valve is communicated with a fourth oil duct arranged in the valve body, so that the reversing valve can be started after hydraulic oil enters, and the valve cavity is communicated with the main oil duct.
Furthermore, a throttle valve is arranged at the joint of the main oil duct and the valve cavity, and the throttle valve is mainly used for controlling the time of oil passing through the main oil duct, so that the impact caused by the fact that the valve rod of the amplifying valve is quickly closed is reduced.
Furthermore, the communicating ports of the first oil duct, the second oil duct and the valve cavity are throttle ports.
In a first aspect, a steering hydraulic control system is disclosed, comprising: the device comprises a load sensing steering gear, a steering pump, a pilot pump and a steering oil cylinder. Wherein: and the L oil port of the load sensing steering gear is connected with the second oil port of the flow amplifying valve, and the R oil port of the load sensing steering gear is connected with the first oil port of the flow amplifying valve. And the Ls oil port of the load sensing steering gear is simultaneously communicated with the third oil duct and the fourth oil duct of the flow amplifying valve, so that hydraulic oil can conveniently start the reversing valve after entering. The steering pump is communicated with an oil inlet of a priority valve in the flow amplifying valve, and the pilot pump is communicated with the load sensing steering gear so as to convey hydraulic oil to the load sensing steering gear. And the steering oil cylinder is communicated with an oil outlet of an amplification valve in the flow amplification valve.
Further, the steering pump and the pilot pump are communicated with the oil pan so as to provide oil.
Furthermore, the first oil port and the second oil port are respectively connected with a joint so as to be conveniently connected with an oil conveying pipe between the load sensing steering gears.
Furthermore, the third oil duct and the fourth oil duct are respectively connected with a joint so as to be conveniently connected with an oil delivery pipe at an Ls port of the load sensing steering gear.
Compared with the prior art, the invention has the following beneficial effects: the flow amplifying valve effectively solves the problem that the whole vehicle shakes left and right when the existing flow amplifying steering hydraulic system encounters uneven rotating speed of a steering wheel and stops rotating, improves driving comfort and safety, and prolongs the service life of relevant parts. The reason is as follows: taking a steering wheel for right steering as an example, when the vehicle is suddenly stopped in right steering, an L oil port, an R oil port and an Ls oil port of the load sensing steering gear are all closed, so that no oil liquid flows in the main oil duct, and the valve rod of the amplification valve resets under the action of the control spring. Meanwhile, as the Ls oil port is also closed, the pressure in the third oil duct and the fourth oil duct is zero, and the first reversing valve and the second reversing valve are closed, the first oil duct cannot pass through oil, the oil in the valve cavity at the right end of the valve rod of the amplification valve only returns to the valve cavity at the left end of the valve rod of the amplification valve through the main oil duct, the size of the throttling port of the throttle valve is changed to limit the return time of the valve rod of the amplification valve, and therefore the impact caused by the rapid closing of the valve rod of the amplification valve is reduced.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this specification, are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate exemplary embodiments of the invention and together with the description serve to explain the invention and not to limit the invention.
FIG. 1 is a front view of a flow amplifying valve in an embodiment of the present invention.
FIG. 2 is a top view of a flow amplifying valve in a right turn in an embodiment of the present invention.
Fig. 3 is a schematic structural diagram of a steering hydraulic control system in an embodiment of the invention.
FIG. 4 is a top view of the flow amplifying valve in a left turn in an embodiment of the present invention.
The labels in the figures represent: the hydraulic control valve comprises a valve body 1, an amplifying valve rod 2, a control spring 3, a main oil duct 4, a first oil duct 5, a second oil duct 6, a first reversing valve 7, a second reversing valve 8, a valve cavity 9, a first oil port 10, a second oil port 11, a third oil duct 12, a fourth oil duct 13, a throttle valve 14, a load sensing steering gear 15, a steering pump 16, a pilot pump 17, a steering oil cylinder 18, an oil pan 19, a priority valve 20, an oil inlet 21, an oil outlet 22 and an A-flow amplifying valve.
Detailed Description
It is to be understood that the following detailed description is exemplary and is intended to provide further explanation of the invention as claimed. Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs.
For convenience of description, the words "up", "down", "left" and "right" in the present invention, if any, merely indicate that the directions of movement are consistent with those of the drawings, and do not limit the structure, but merely facilitate the description of the invention and simplify the description, rather than indicate or imply that the referenced device or element needs to have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the invention. Reference will now be made in detail to the embodiments illustrated in the drawings.
Referring to fig. 1 and 2, an example flow amplifying valve includes: the valve comprises a valve body 1, an amplification valve rod 2, a control spring 3, a main oil duct 4, a first oil duct 5, a second oil duct 6, a first reversing valve 7 and a second reversing valve 8. The arrows in fig. 1 indicate the direction of oil flow. The flow amplifying valves of the following embodiments are based on a conventional ZLF25E type flow amplifying valve, and reference is made to this type of flow amplifying valve for a part not described.
The valve body 1 is horizontally arranged, a valve cavity 9 which is horizontally distributed from left to right is formed in the valve body 1, the amplification valve rod 2 is horizontally arranged in the valve cavity 9, and a first oil port 10 and a second oil port 11 are respectively formed at two ends of the valve body 1 through two ports of the valve cavity 9, so that hydraulic oil can conveniently enter and exit. The control spring 3 is sleeved on the outer wall of one end of the amplification valve rod 2, so that the amplification valve rod 2 is reset.
With continued reference to fig. 1, a main oil gallery 4 is disposed in the valve body 1, a left end of the main oil gallery 4 is communicated with a left end of the valve cavity 9, and a right end of the main oil gallery 4 is communicated with a right end of the valve cavity 9, so that hydraulic oil entering one end of the valve cavity 9 from the first oil port 10 or the second oil port 11 flows to the other end of the valve cavity 9 through the main oil gallery 4.
The upper end of the first oil duct 5 is communicated with the right part of the main oil duct 4, the lower end of the first oil duct 5 is communicated with the right part of the valve cavity 9, the upper end of the second oil duct 6 is communicated with the left part of the main oil duct 4, and the lower end of the second oil duct 6 is communicated with the left part of the valve cavity 9. The first reversing valve 7 is arranged in the first oil duct 5, the second reversing valve 8 is arranged in the second oil duct 6, the first reversing valve 7 is communicated with the third oil duct 12 arranged in the valve body 1, and the second reversing valve 8 is communicated with the fourth oil duct 13 arranged in the valve body 1, so that the reversing valve is started after hydraulic oil enters, and the valve cavity 9 is communicated with the main oil duct 4.
In another embodiment, the communication ports of the first oil passage 5 and the second oil passage 6 with the valve cavity 9 are throttle ports. A throttle valve 14 is arranged at the joint of the main oil passage 4 and the valve cavity 9.
Referring to fig. 1 to 3, a steering hydraulic control system is exemplified, including: the flow rate amplification valve a, the load sensing steering gear 15, the steering pump 16, the pilot pump 17, and the steering cylinder 18 of the above embodiment example. Wherein: the load sensing steering gear 15 is a load sensing steering gear, an L oil port of the load sensing steering gear is connected with the first oil port 10 of the flow amplifying valve, and an R oil port of the load sensing steering gear is connected with the second oil port 11 of the flow amplifying valve a. The Ls oil port of the load sensing steering gear is simultaneously communicated with the third oil duct 12 and the fourth oil duct 13 of the flow amplifying valve A, so that the first reversing valve 7 and the second reversing valve 8 can be started after hydraulic oil enters. The steering pump 16 is communicated with an oil inlet 21 of a priority valve 20 in the flow amplifying valve A, and the pilot pump 17 is communicated with the load sensing steering gear 15 so as to convey hydraulic oil into the load sensing steering gear 15. The steering oil cylinder 18 is connected with an amplifying valve oil outlet 22 in the flow amplifying valve A, and the oil inlet 21 and the amplifying valve oil outlet 22 both extend to the outer surface of the valve body 1 through the valve body. The steering pump 16 and the pilot pump 17 are both connected with an oil pan 19 so as to provide oil for the steering pump 16 and the pilot pump 17.
Referring to fig. 1, in another embodiment, joints are respectively connected to the first oil port 10 and the second oil port 11 to facilitate the oil pipeline connection with the load sensing steering gear 15.
Referring to fig. 1 to 3, taking a right steering of the loader as an example, the use method of the steering hydraulic control system is as follows:
during the operation of the loader, the incoming oil of the pilot pump 17 enters the load sensing steering gear 15, during the right steering of the steering wheel, the incoming oil of the Ls oil port of the load sensing steering gear 15 enters the third oil passage 12 and the fourth oil passage 13, and the first reversing valve 7 and the second reversing valve 8 are opened under the pressure of the hydraulic oil. Meanwhile, the oil from the R port of the load sensing steering gear 15 enters the right end chamber of the valve chamber 9 through the first port 10, and then pushes the amplification valve rod 2 to move leftward, so that the lower port of the first oil passage 5 is opened and is communicated with the valve chamber 9. The oil entering the right end of the valve cavity 9 enters the main oil gallery 4 through two paths of the throttle valve 14 and the first reversing valve 7 and then flows into the left end chamber of the valve cavity 9, and then returns to the load sensing steering gear 15 from the second oil port 11 and the L oil port of the load sensing steering gear 15, at this time, because the amplifying valve rod 2 moves leftwards, the lower port of the second oil gallery 6 is blocked, and therefore, although the second reversing valve 8 is opened, the oil from the main oil gallery 4 cannot enter the left end chamber of the valve cavity 9 through the second oil gallery 6. Meanwhile, the size of the opening amount of the amplification valve stem 2 is determined by the hydraulic pressure difference between the first oil port 10 and the second oil port 11, that is, the larger the oil flow from the first oil port 10 is, the larger the compression amount of the control spring 3 is, the larger the opening amount of the amplification valve stem 2 is. In the process, as the valve rod 2 of the amplification valve moves leftwards, the valve cavity 9 of the valve rod 2 of the amplification valve is communicated with the valve cavity of the priority valve rod 20, the incoming oil of the steering pump 16 passes through the oil inlet 21 in the flow amplification valve, then enters the valve cavity 9 of the valve rod 2 of the amplification valve through the connecting channel, is discharged from the oil outlet 22 of the amplification valve, and enters the steering oil cylinder 18 to enable the whole loader to rotate rightwards.
When the vehicle is suddenly stopped in right steering, the L oil port and the R oil port of the load sensing steering gear 15 are closed and the Ls oil port is communicated for oil return because no steering acting force exists, and the amplifying valve rod 2 is reset under the action of the control spring 3. Meanwhile, the Ls oil port is communicated with the oil return, the pressure in the third oil duct 12 and the fourth oil duct 13 is zero, and the first reversing valve 7 and the second reversing valve 8 are closed, so that the first oil duct 5 cannot pass through oil, the oil in the valve cavity at the right end of the amplification valve rod 2 only returns to the valve cavity at the right end of the amplification valve rod 2 through the main oil duct 4, the time of the oil flowing from the main oil duct 4 is limited by the size of the throttling port of the throttling valve 14, the reset time of the amplification valve rod 2 is further controlled, and the impact caused by the rapid closing of the amplification valve rod 2 is reduced. When the situation that the steering speed is not uniform is met, based on the same principle, the valve rod 2 of the amplification valve cannot be suddenly or quickly reset but has certain reset time, so that the problem of left-right shaking of the whole vehicle is solved.
In the case of a left turn of the loader (see fig. 3 and 4, the arrows in fig. 4 indicate the oil flow direction), the process is substantially the same as in the right turn, except that: oil in the load sensing steering gear 15 enters a left end chamber of the valve cavity 9 from the L oil port, the amplifying valve rod 2 moves rightwards, and the oil flows out of the right end of the valve cavity 9 and returns to the load sensing steering gear 15.
Finally, it should be understood that any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention. Although the embodiments of the present invention have been described with reference to the accompanying drawings, it is not intended to limit the scope of the invention, and it should be understood by those skilled in the art that various modifications and variations can be made without inventive changes in the technical solutions of the present invention.
Claims (6)
1. A flow amplifying valve, comprising: the oil-gas amplification valve comprises a valve body, an amplification valve rod, a control spring, a main oil duct, a first oil duct, a second oil duct, a first reversing valve and a second reversing valve; wherein: the valve rod of the amplification valve is horizontally arranged in a valve cavity of the valve body, and a first oil port and a second oil port are respectively formed at two ends of the valve body by two ports of the valve cavity; the control spring is sleeved on the outer wall of one end of the amplifying valve rod; the main oil gallery is positioned in the valve body, and two ends of the main oil gallery are respectively communicated with two ends of the valve cavity; the upper end of the first oil duct is communicated with the right part of the main oil duct, the lower end of the first oil duct is communicated with the right part of the valve cavity, the upper end of the second oil duct is communicated with the left part of the main oil duct, and the lower end of the second oil duct is communicated with the left part of the valve cavity; the first reversing valve is arranged in the first oil duct, the second reversing valve is arranged in the second oil duct, the first reversing valve is communicated with a third oil duct arranged in the valve body, the second reversing valve is communicated with a fourth oil duct arranged in the valve body, and a throttle valve is arranged at the joint of the main oil duct and the valve cavity.
2. The flow amplifying valve of claim 1, wherein the communication ports of the first and second oil passages with the valve chamber are chokes.
3. A steering hydraulic control system, characterized by comprising: a load sensing steering gear, a steering pump, a pilot pump, a steering cylinder and a flow amplifying valve according to claim 1 or 2; wherein: an L oil port of the load sensing steering gear is connected with a second oil port of the flow amplifying valve, and an R oil port of the load sensing steering gear is connected with a first oil port of the flow amplifying valve; the Ls oil port of the load sensing steering gear is simultaneously communicated with the third oil duct and the fourth oil duct of the flow amplifying valve; the steering pump is communicated with an oil inlet of a priority valve in the flow amplifying valve, the pilot pump is communicated with the load sensing steering gear, and the steering oil cylinder is communicated with an oil outlet of the amplifying valve in the flow amplifying valve.
4. The steering hydraulic control system of claim 3, wherein the steering pump and the pilot pump are both in communication with an oil pan.
5. The steering hydraulic control system according to claim 3 or 4, wherein the first oil port and the second oil port are respectively connected with a joint for communicating with an oil delivery pipe between the load sensing steering gear.
6. The steering hydraulic control system according to claim 3 or 4, characterized in that the third oil passage and the fourth oil passage are respectively connected with a joint for communicating with an oil delivery pipe of an Ls port of the load sensing steering gear.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210484550.XA CN114576228B (en) | 2022-05-06 | 2022-05-06 | Flow amplifying valve and steering hydraulic control system thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210484550.XA CN114576228B (en) | 2022-05-06 | 2022-05-06 | Flow amplifying valve and steering hydraulic control system thereof |
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| Publication Number | Publication Date |
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| CN114576228A CN114576228A (en) | 2022-06-03 |
| CN114576228B true CN114576228B (en) | 2022-07-22 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202210484550.XA Active CN114576228B (en) | 2022-05-06 | 2022-05-06 | Flow amplifying valve and steering hydraulic control system thereof |
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Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3566749A (en) * | 1968-03-13 | 1971-03-02 | Caterpillar Tractor Co | Hydraulic flow amplifier valve |
| US4006663A (en) * | 1973-02-07 | 1977-02-08 | Danfoss A/S | Hydraulic control means, especially a steering means |
| CN2477883Y (en) * | 2001-04-29 | 2002-02-20 | 山东工程机械厂 | Flow switching control valve |
| CN1361362A (en) * | 2000-12-28 | 2002-07-31 | 浙江临海海宏集团有限公司 | Priority-type flow rate enlarging and merging valve |
| CN101255878A (en) * | 2007-09-21 | 2008-09-03 | 兰州理工大学 | Energy-saving vibration-reduction type flux amplification valve |
| CN101255880A (en) * | 2007-12-10 | 2008-09-03 | 兰州理工大学 | Meso position unloading type flux amplification valve |
| CN101255879A (en) * | 2007-12-10 | 2008-09-03 | 兰州理工大学 | Steering preference type flux amplification valve |
| CN204082733U (en) * | 2014-07-16 | 2015-01-07 | 浙江海宏液压科技股份有限公司 | Preference type flux amplification valve |
| CN105626615A (en) * | 2016-02-29 | 2016-06-01 | 浙江高宇液压机电有限公司 | Steering feedback type flow amplification valve |
| CN106609779A (en) * | 2017-02-08 | 2017-05-03 | 雷沃重工股份有限公司 | Flow amplifying valve and loading machine variable steering hydraulic system |
-
2022
- 2022-05-06 CN CN202210484550.XA patent/CN114576228B/en active Active
Patent Citations (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3566749A (en) * | 1968-03-13 | 1971-03-02 | Caterpillar Tractor Co | Hydraulic flow amplifier valve |
| US4006663A (en) * | 1973-02-07 | 1977-02-08 | Danfoss A/S | Hydraulic control means, especially a steering means |
| CN1361362A (en) * | 2000-12-28 | 2002-07-31 | 浙江临海海宏集团有限公司 | Priority-type flow rate enlarging and merging valve |
| CN2477883Y (en) * | 2001-04-29 | 2002-02-20 | 山东工程机械厂 | Flow switching control valve |
| CN101255878A (en) * | 2007-09-21 | 2008-09-03 | 兰州理工大学 | Energy-saving vibration-reduction type flux amplification valve |
| CN101255880A (en) * | 2007-12-10 | 2008-09-03 | 兰州理工大学 | Meso position unloading type flux amplification valve |
| CN101255879A (en) * | 2007-12-10 | 2008-09-03 | 兰州理工大学 | Steering preference type flux amplification valve |
| CN204082733U (en) * | 2014-07-16 | 2015-01-07 | 浙江海宏液压科技股份有限公司 | Preference type flux amplification valve |
| CN105626615A (en) * | 2016-02-29 | 2016-06-01 | 浙江高宇液压机电有限公司 | Steering feedback type flow amplification valve |
| CN106609779A (en) * | 2017-02-08 | 2017-05-03 | 雷沃重工股份有限公司 | Flow amplifying valve and loading machine variable steering hydraulic system |
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| Title |
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| 《新型高压流量放大阀在轮式装载机转向液压系统中的设计研究》;蔡铮等;《工程机械》;20211130(第11期);全文 * |
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| CN114576228A (en) | 2022-06-03 |
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