CN105508334B - Electricity drives polygon overflow pulsation attenuation control system and polygon overflow system - Google Patents
Electricity drives polygon overflow pulsation attenuation control system and polygon overflow system Download PDFInfo
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- CN105508334B CN105508334B CN201511026009.0A CN201511026009A CN105508334B CN 105508334 B CN105508334 B CN 105508334B CN 201511026009 A CN201511026009 A CN 201511026009A CN 105508334 B CN105508334 B CN 105508334B
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- 230000010349 pulsation Effects 0.000 title claims abstract description 60
- 230000005611 electricity Effects 0.000 title abstract 2
- 239000012530 fluid Substances 0.000 claims abstract description 37
- 239000007788 liquid Substances 0.000 claims description 16
- 230000007246 mechanism Effects 0.000 claims description 10
- 238000013016 damping Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 description 7
- 239000000919 ceramic Substances 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 239000006096 absorbing agent Substances 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
Classifications
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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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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/04—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor
- F16K31/041—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves
- F16K31/042—Actuating devices; Operating means; Releasing devices electric; magnetic using a motor for rotating valves with electric means, e.g. for controlling the motor or a clutch between the valve and the motor
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
This application involves a kind of electricity to drive polygon overflow pulsation attenuation control system and polygon overflow system.Control system includes pressure sensor, controller, executing agency and polygon overflow valve；Wherein, the fluid pressure signal that controller is used to acquire based on pressure sensor generates the control instruction of control executing agency；Polygon overflow valve includes spool and valve core housing, m through-hole is offered on spool to form bypass overflow inlet, n through-hole is offered on valve core housing to form bypass overflow outlet, spool is coaxially disposed with valve core housing, and spool is rotated around rotary shaft, so that at least one bypass overflow inlet forms overflow ducts at least one bypass overflow outlet conducting；Executing agency is used to rotate around rotary shaft with movable valve plug and/or be moved back and forth along the direction of rotary shaft.According to the scheme of the application, the movement by controlling spool makes overflow inlet and overflow export to match to form overflow ducts, can offset the flow pulsation generated in main pipeline at least partially.
Description
Technical Field
The application relates to the field of hydraulic systems, in particular to an electrically-driven multilateral overflow pulsation attenuation control system and a multilateral overflow system.
Background
The hydraulic system has been widely used in many important industrial sectors such as aviation, aerospace, ships and the like due to its advantages of large power density, large load-resistant rigidity and the like. With the development of hydraulic systems towards high speed, high pressure and high power, the problems of vibration and noise of hydraulic energy pipeline systems become more and more serious, and the problems become bottlenecks which restrict the development of hydraulic systems towards high pressure and low noise.
At present, most of hydraulic systems adopt an axial plunger pump to provide hydraulic energy, because the axial plunger pump has the advantages of high output pressure, high working efficiency, high reliability and the like. However, the axial plunger pump inevitably generates fluid pulsation due to its own structure and operation principle. The fluid pulsations in turn cause pressure pulsations due to the inevitable presence of hydraulic resistances inside the pump and in the pipe system. The damage of the pressure pulsation to the hydraulic energy pipeline system is usually expressed in the form of fluid-solid coupling vibration, that is, the pressure pulsation generates pipeline vibration, which in turn affects the pressure pulsation. Such pipe vibrations due to fluid-solid coupling tend to cause fatigue failure and radiated noise in the piping system. Therefore, the hydraulic fluid pulsation is the fundamental cause of structural vibration and radiation noise of the hydraulic energy pipeline system.
Due to the inherent structure and the working principle of the axial plunger pump, discontinuity exists in the oil suction process, fluid pulsation also exists in an oil suction pipe of a hydraulic energy pipeline system due to the discontinuity, and the problems of pipeline vibration and radiation noise caused by the fluid pulsation are also not negligible. Therefore, the method has very important practical significance for simultaneously inhibiting the fluid pulsation in the oil suction and discharge pipeline of the hydraulic system.
The active vibration control has become an important development direction for the fluid pulsation control of the pipeline system due to the advantages of strong self-adaptive capacity and the like. The active control system for fluid pulsation mainly comprises a sensor, a controller and an actuator. According to different types of actuators, the research on the active control of the fluid pulsation of the pipeline system at home and abroad can be divided into three categories: the first type is that an intelligent material actuator arranged outside the pipe wall is utilized to generate control force on the pipe wall to cause elastic deformation of the pipe wall, so that fluid pulsation waves are generated in the pipeline and offset with the original fluid pulsation; the second type is that the actuator acting on the fluid is used to directly generate fluid pulsation waves to counteract the original fluid pulsation in the pipeline system; the third type is to use a hydraulic valve to generate the original flow pulsation of the overflow flow control.
For the third method, the characteristics are summarized as follows:
the fluid pulsation active control based on the bypass overflow principle is suitable for the pulsation active control of a high-pressure hydraulic system, and because the intelligent material for pushing the valve core to move only needs to output small force to overcome friction, valve core inertia and hydraulic force, and does not need to bear large load caused by high-pressure fluid; in addition, as can be seen from the throttle formula, after a large pressure amplification, a relief flow rate equal to the pulsation flow rate of the hydraulic pump can be generated when the opening of the hydraulic valve is small. Therefore, the vibration damping valve has lower energy consumption and smaller volume compared with the fluid actuator. However, the conventional active control method based on the bypass overflow principle requires that the frequency of the piezoelectric ceramic vibration damping valve can keep up with the fluid pulsation frequency, so as to generate the overflow flow rate which is mutually offset with the pulsation flow rate of the hydraulic pump. As is known, the fluid pulsations generated by a piston pump contain a plurality of sinusoidal frequency components whose frequencies are distributed over the fundamental frequency and its higher multiples, these frequencies being proportional to the rotational speed of the pump. With the development of a hydraulic energy system (particularly an airplane hydraulic energy system) towards high pressure and high flow, the rotating speed of an axial plunger pump becomes higher and higher, so that the fundamental frequency of fluid pulsation reaches the working frequency limit of a piezoelectric ceramic actuator, and the high-order frequency multiplication of the fluid pulsation is far beyond the frequency response range of the piezoelectric ceramic actuator. Therefore, the vibration absorber bandwidth cannot meet the increasing fluid pulsation frequency requirement of the hydraulic system, and the bottleneck of applying the traditional fluid pulsation active control method based on the bypass overflow principle in the high-speed hydraulic system is formed.
Disclosure of Invention
A brief summary of the present application is provided below in order to provide a basic understanding of some aspects of the present application. It should be understood that this summary is not an exhaustive overview of the present application. It is not intended to identify key or critical elements of the application or to delineate the scope of the application. Its sole purpose is to present some concepts in a simplified form as a prelude to the more detailed description that is discussed later.
It is a primary object of the present application to provide an electrically driven multiple-leg spill pulsation attenuation control system and a multiple-leg spill system, which are intended to solve the technical problems described above.
In a first aspect, the application provides an electrically-driven multilateral overflow pulsation attenuation control system, which comprises a pressure sensor, a controller, an actuating mechanism and a multilateral overflow valve; the controller is used for generating a control instruction for controlling the actuating mechanism based on the fluid pressure signal acquired by the pressure sensor; the multilateral overflow valve comprises a valve core and a valve core sleeve, wherein m through holes are formed in the valve core to form a bypass overflow inlet, n through holes are formed in the valve core sleeve to form a bypass overflow outlet, the valve core and the valve core sleeve are coaxially arranged, and the valve core rotates around a rotating shaft so that at least one bypass overflow inlet is communicated with at least one bypass overflow outlet to form an overflow channel; the actuating mechanism is used for driving the valve core to rotate around the rotating shaft and/or reciprocate along the direction of the rotating shaft.
In some embodiments, the controller is configured to generate a control command to control the actuator to drive the valve element to move when the fluid pressure signal collected by the pressure sensor is greater than a preset pressure threshold value, so that the at least one bypass overflow inlet is communicated with the at least one bypass overflow outlet to form the at least one overflow channel.
In some embodiments, the control commands include axial motion control commands and rotational motion control commands; the actuating mechanism comprises an electromagnetic actuator and a motor; the electromagnetic actuator is used for generating a force for driving the valve core to reciprocate along the direction of the rotating shaft based on the axial motion control instruction; the motor is used for generating torque for driving the valve core to rotate around the rotating shaft based on the rotary motion control command.
In some embodiments, the valve core rotates periodically around the rotation axis, and each bypass overflow inlet is communicated with each bypass overflow outlet in a matching way once in each movement period.
In some embodiments, the valve core and the valve core sleeve are both hollow cylinders, and the outer wall of the valve core is matched with the inner wall of the valve core sleeve.
In some embodiments, each bypass spill outlet is connected to the tank such that oil entering the bypass spill passageway flows into the tank.
In a second aspect, the present application also provides a multilateral overflow system, comprising a main oil-liquid channel and an electrically driven multilateral overflow pulsation attenuation control system as described above; the pressure sensor is arranged in the main oil liquid channel and used for acquiring oil liquid pressure in the main oil liquid channel as an oil liquid pressure signal.
Adopt electric drive multilateral overflow pulsation attenuation control system and multilateral overflow system of this application, seted up a plurality of overflow outlets and seted up a plurality of overflow inlets on the case, make overflow inlet and overflow outlet cooperate and form overflow channel through the motion of control case, can offset the flow pulsation that produces in the trunk line partially at least.
In addition, in some embodiments of the present application, the controller may control the valve core to move periodically, and in one movement cycle, a plurality of relief channels may be formed between the valve core and the valve core sleeve of the polygonal relief valve, so that even in a case where the movement frequency of the valve core is low, a large amount of liquid flow caused by flow pulsation can be released in one movement cycle.
In addition, in some embodiments of the present application, the controller may also control the relative positional relationship between the spool and the spool sleeve to control the amount of oil entering the relief passage.
Drawings
The above and other objects, features and advantages of the present application will be more readily understood by reference to the following description of the embodiments of the present application taken in conjunction with the accompanying drawings. The components in the figures are meant only to illustrate the principles of the present application. In the drawings, the same or similar technical features or components will be denoted by the same or similar reference numerals.
FIG. 1 is a schematic block diagram of one embodiment of an electrically driven polygonal spill pulsation attenuation control system of the present application;
FIG. 2 is a sectional view of the polygonal relief valve in FIG. 1 taken along the axial direction and a sectional view taken perpendicular to the axial direction;
FIG. 3 is a schematic diagram of the flow direction of oil in the polygonal overflow valve of the present application at different times of a cycle;
fig. 4 is a schematic graph of the overflow flow rate generated by the polygonal overflow valve of the present application in one cycle.
Detailed Description
Embodiments of the present application are described below with reference to the drawings. Elements and features described in one drawing or one embodiment of the application may be combined with elements and features shown in one or more other drawings or embodiments. It should be noted that the figures and descriptions have omitted, for the sake of clarity, the representation and description of components and processes that are not relevant to the present application and are known to those of ordinary skill in the art.
Referring to fig. 1, a block diagram 100 of one embodiment of the electrically driven polygonal spill pulsation attenuation control system of the present application is shown.
The polygonal spill pulsation damping control system of the present embodiment includes a pressure sensor 110, a controller 120, an actuator 130, and a polygonal spill valve 140.
The controller 120 is configured to generate a control command for controlling the actuator 130 based on the fluid pressure signal collected by the pressure sensor 110.
The polygonal relief valve 140 includes a spool 142 and a spool case 141. The valve core 141 is provided with m through holes to form a bypass overflow inlet, the valve core sleeve 142 is provided with n through holes to form a bypass overflow outlet, the valve core and the valve core sleeve are coaxially arranged, and the valve core 141 rotates around a rotating shaft so that at least one bypass overflow inlet is communicated with at least one bypass overflow outlet to form an overflow channel.
The actuator 130 is used for driving the valve core 141 to rotate around a rotating shaft and/or reciprocate along the direction of the rotating shaft.
Referring to fig. 2, a sectional view along the axial direction and a sectional view perpendicular to the axial direction of the polygonal overflow valve in the polygonal overflow pulsation attenuation control system of the present application are shown.
In the polygonal overflow valve of this embodiment, the valve core 210 is provided with m through holes 211 to form a bypass overflow inlet, and the valve core sleeve 220 is provided with n through holes 221 to form a bypass overflow outlet. The valve core 210 is coaxially disposed with the valve core sleeve 220 and rotates around the rotation axis, so that at least one bypass overflow inlet and at least one bypass overflow outlet are communicated to form an overflow channel. Here, m is a positive integer, and n is a positive integer greater than 1.
When one of the bypass overflow inlets of the valve core 210 is communicated with the bypass overflow outlet of the valve core sleeve 220 to form an overflow channel, the oil can flow into the overflow channel from the bypass overflow inlet and flow out through the bypass overflow outlet communicated with the bypass overflow inlet in a matching manner.
It should be noted that fig. 1 only schematically shows the case of 1 bypass overflow inlet (i.e., m-1) and 4 bypass overflow outlets (i.e., n-4). The number of bypass overflow inlets and bypass overflow outlets is merely illustrative. After obtaining the technical solution of the polygonal overflow valve in the embodiment of the present application, a person skilled in the art may specifically set the number of bypass overflow inlets according to an actual application scenario, so as to achieve a corresponding overflow flow to offset flow pulsation. Therefore, no matter how many bypass overflow inlets are arranged on the valve core, and no matter how many bypass overflow outlets are arranged on the valve core sleeve, the structure of the multilateral overflow valve disclosed by the application is considered to fall into the protection scope of the application as long as the structure is provided.
In some alternative implementations, the valve core 210 rotates periodically around the rotation axis, and each bypass overflow inlet is communicated with each bypass overflow outlet once in cooperation with each movement cycle. In these alternative implementations, one revolution (360 °) of the spool about the axis of rotation is one period of movement of the spool.
In these optional implementations, m bypass overflow inlets are disposed on the valve core 210, n bypass overflow outlets are disposed on the valve core sleeve 220, and each bypass overflow inlet is matched with each bypass overflow outlet to be conducted once in a movement cycle of the valve core 210. In one movement period, m × n overflow channels are formed in a time-sharing manner. Therefore, when the movement frequency of the valve core 210 in periodic movement is low, a large overflow flow can be generated, so that the fluid entering the valve core and generated by flow pulsation is discharged outside the polygonal overflow valve through the overflow channel, and the fluid pulsation is counteracted.
In some alternative implementations, the valve core 210 and the valve core sleeve 220 can both be hollow cylinders, and the outer wall of the valve core 210 mates with the inner wall of the valve core sleeve 220.
Referring back to fig. 1, in some alternative implementations, the controller 120 is further configured to generate a control command to control the actuator 130 to move the valve element 142 such that the at least one bypass overflow inlet is communicated with the at least one bypass overflow outlet to form at least one overflow channel when the fluid pressure signal collected by the pressure sensor 110 is greater than a preset pressure threshold.
In some alternative implementations, the control commands may include axial motion control commands and rotational motion control commands.
In these alternative implementations, the actuator 130 may include an electromagnetic actuator 131 and an electric motor 132. The electromagnetic actuator 131 may be configured to generate a force that reciprocates the spool 142 in the direction of the rotation axis based on the axial motion control command. The motor 132 may be used to generate a torque that rotates the spool 142 about the axis of rotation based on the rotational motion control command.
In some applications, the axial motion control command may control the relative position between the spool 142 and the spool sleeve 141 to control the volume of the relief channels formed, and thus the amount of fluid entering each relief channel.
Further, similarly, the rotational motion control command may control the angular velocity and/or angle at which the spool 142 rotates about the axis of rotation to control the number of times the spill passageway is formed, and thus the amount of fluid that enters the spill passageway over a period of time.
In some alternative implementations, each bypass spill outlet is connected to tank 20 such that oil entering the bypass spill passageway flows into tank 20, thereby attenuating flow pulsations into spool 142 of polygonal spill valve 140.
In a second aspect, the present application also provides a multilateral overflow system, comprising a main oil-liquid channel and an electrically driven multilateral overflow pulsation attenuation control system as described above; the pressure sensor is arranged in the main oil liquid channel and used for acquiring oil liquid pressure in the main oil liquid channel as an oil liquid pressure signal.
In the following, how the polygonal relief valve and the polygonal relief system of the present application attenuate pulsation of fluid in the main fluid passage will be described with reference to fig. 3 and 4, taking m-1 and n-4 as examples.
As shown in fig. 3, at the first time in one movement cycle of the valve body rotational movement, the bypass overflow inlet 311 of the valve body is connected to the first bypass overflow outlet 321 on the valve body cover to form an overflow passage.
At a second time in one movement cycle of the valve core rotation movement, the bypass overflow inlet 311 of the valve core is communicated with the second bypass overflow outlet 322 on the valve core sleeve to form an overflow channel.
At a third time in one movement cycle of the valve core rotation movement, the bypass overflow inlet 311 of the valve core is communicated with the third bypass overflow outlet 323 on the valve core sleeve to form an overflow channel.
At a fourth time in one movement cycle of the valve core rotation movement, the bypass overflow inlet 311 of the valve core is communicated with the fourth bypass overflow outlet 324 on the valve core sleeve to form an overflow channel.
Thus, four bypass relief passages may be formed at different times during one movement cycle of the rotational movement of the spool.
In FIG. 4, T1Flow pulsation Q in main oil-liquid channeldFundamental frequency f of1Reciprocal of (1), T2The motion period of the valve core of the polygonal overflow valve is shown.
In a movement period of a valve core in the polygonal overflow valve, the valve core rotates at a constant speed, and in the movement period, the displacement of the valve core is x. If each bypass overflow inlet in the overflow valve has the same shape, the distance (included angle) between every two adjacent bypass overflow inlets is equal, each bypass overflow outlet in the overflow valve has the same shape, and the distance (included angle) between every two adjacent bypass overflow outlets is equal, m × n overflow channels are generated in one movement period of the valve core, and the overflow flow Q generated by each overflow channel0Are equal, and each Q0Evenly distributed along the time axis.
Thus, assume the flow pulsation Q in the main oil passagedHas a fundamental frequency of f1That is, 1/f per interval1Then a Q is generatedd. The method can be realized by setting the movement period of a valve core in the polygonal overflow valve:
T2＝m×n/f1(1)
so that m multiplied by n flow pulses Q can be attenuated in one movement period of the valve coredTherefore, the movement frequency of the actuating mechanism and the valve core can be greatly reduced.
Or, when T is2The number of the bypass overflow inlets and/or the bypass overflow outlets can also be designed by the above formula (1) when the bypass overflow outlets are fixed values, so as to weaken a plurality of flow pulsation Q in one movement period of the polygonal overflow valvedThe technical effect of (1).
In addition, the valve core and the valve core can be controlled by an axial motion control command output by the controllerRelative position between the sleeves to control the volume of the overflow channels formed and thus the amount of fluid (Q) entering each overflow channel0)。
It should be noted that the overflow flow generated by the polygonal overflow valve in fig. 4 in one cycle is only schematic. Those skilled in the art can conceive of the technical solutions of the polygonal overflow valve and the electrically-driven polygonal overflow pulsation attenuation control system of the present application by adjusting the axial movement control command to adjust the flow Q generated each time the bypass overflow inlet and the bypass overflow outlet are communicated0And the time for conducting the bypass overflow inlet and the bypass overflow outlet is adjusted by adjusting the rotary motion control command. Therefore, the flow rate Q generated when the bypass overflow inlet and the bypass overflow outlet are communicated each time0Whether the two bypass overflow inlets and the bypass overflow outlets are the same or not is also not determined, and as long as the structure of the multi-edge overflow valve and the electrically-driven multi-edge overflow pulsation attenuation control system disclosed by the application is adopted, the two bypass overflow inlets and the two bypass overflow outlets are considered to fall into the protection scope of the application.
The above description is only a preferred embodiment of the application and is illustrative of the principles of the technology employed. It will be appreciated by a person skilled in the art that the scope of the invention as referred to in the present application is not limited to the embodiments with a specific combination of the above-mentioned features, but also covers other embodiments with any combination of the above-mentioned features or their equivalents without departing from the inventive concept. For example, the above features may be replaced with (but not limited to) features having similar functions disclosed in the present application.
Claims (6)
1. An electrically-driven multilateral overflow pulsation attenuation control system is characterized by comprising a pressure sensor, a controller, an actuating mechanism and a multilateral overflow valve;
wherein,
the controller is used for generating a control instruction for controlling the actuating mechanism based on the fluid pressure signal collected by the pressure sensor;
the multilateral overflow valve comprises a valve core and a valve core sleeve, wherein m through holes are formed in the valve core to form a bypass overflow inlet, n through holes are formed in the valve core sleeve to form a bypass overflow outlet, the valve core and the valve core sleeve are coaxially arranged, and the valve core rotates around a rotating shaft so that at least one bypass overflow inlet is communicated with at least one bypass overflow outlet to form an overflow channel;
the actuating mechanism is used for driving the valve core to rotate around the rotating shaft and/or reciprocate along the direction of the rotating shaft;
the valve core rotates around the rotating shaft periodically, and in each movement period, each bypass overflow inlet is communicated with each bypass overflow outlet in a matched mode once.
2. The electrically driven polygonal flooding pulsation attenuation control system of claim 1, wherein:
the controller is used for generating a control instruction when the fluid pressure signal acquired by the pressure sensor is greater than a preset pressure threshold value so as to control the actuating mechanism to drive the valve core to move, so that at least one bypass overflow inlet is communicated with at least one bypass overflow outlet to form at least one overflow channel.
3. The electrically driven polygonal flooding pulsation attenuation control system according to claim 2, characterized in that:
the control command comprises an axial motion control command and a rotary motion control command;
the actuating mechanism comprises an electromagnetic actuator and a motor;
the electromagnetic actuator is used for generating a force for driving the valve core to reciprocate along the direction of the rotating shaft based on the axial motion control command;
the motor is used for generating torque for driving the valve core to rotate around the rotating shaft based on the rotating motion control command.
4. The electrically driven polygonal flooding pulsation attenuation control system of claim 1, wherein:
the valve core and the valve core sleeve are both hollow cylinders, and the outer wall of the valve core is matched with the inner wall of the valve core sleeve.
5. The electrically driven polygonal flooding pulsation damping control system according to any one of claims 1 to 4, characterized in that:
each bypass overflow outlet is connected to a tank so that oil entering the overflow passage flows into the tank.
6. A multilateral overflow system, characterized by comprising a main oil passage and an electrically driven multilateral overflow pulsation attenuation control system according to any one of claims 1 to 5;
the pressure sensor is arranged in the main oil-liquid channel and used for collecting oil-liquid pressure in the main oil-liquid channel as an oil-liquid pressure signal.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201511026009.0A CN105508334B (en) | 2015-12-31 | 2015-12-31 | Electricity drives polygon overflow pulsation attenuation control system and polygon overflow system |
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| CN201511026009.0A CN105508334B (en) | 2015-12-31 | 2015-12-31 | Electricity drives polygon overflow pulsation attenuation control system and polygon overflow system |
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| CN105508334B true CN105508334B (en) | 2018-07-13 |
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| CN105465080B (en) * | 2015-12-31 | 2017-10-27 | 北京航空航天大学 | Polygon overflow system |
| CN108814380B (en) * | 2018-07-03 | 2024-06-28 | 河北正一电器科技有限公司 | Rotary gear switch for bathing machine |
| CN109458460B (en) * | 2018-11-19 | 2019-09-24 | 袁海环 | High pressure air flow controls valve |
| CN113266624A (en) * | 2021-05-17 | 2021-08-17 | 南京航空航天大学 | Rotary valve for high-frequency pulse air pressure modulation |
| CN115617085B (en) * | 2022-12-19 | 2023-05-02 | 星宇电子(宁波)有限公司 | High-pressure gas pressure control valve |
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| CN201982744U (en) * | 2010-12-07 | 2011-09-21 | 上海诺玛液压系统有限公司 | Overflow valve for preventing pressure pulsation impact |
| CN102168671A (en) * | 2011-04-25 | 2011-08-31 | 许宏 | Electrical control variable plunger pump and pump control hydraulic system thereof |
| CN202023797U (en) * | 2011-05-06 | 2011-11-02 | 三一重工股份有限公司 | Pumping mechanism and pulse vibration absorption device thereof, and concrete pumping machine |
| CN102506031B (en) * | 2011-12-31 | 2015-07-01 | 北京航空航天大学 | Hydraulic pipeline fluid pulse active inhibition method based on bilateral overflow principle |
| DE112012005636T5 (en) * | 2012-01-11 | 2014-10-09 | Hitachi Construction Machinery Co., Ltd. | Drive system for closed hydraulic circuit |
| JP5740558B2 (en) * | 2012-01-12 | 2015-06-24 | パナソニックＩｐマネジメント株式会社 | Valve device |
| JP5771291B2 (en) * | 2012-01-31 | 2015-08-26 | 日立建機株式会社 | Hydraulic closed circuit system |
| CN203572717U (en) * | 2013-09-17 | 2014-04-30 | 深圳市瑞格尔仪器有限公司 | High-frequency pulse generator |
| CN103982705B (en) * | 2014-05-09 | 2016-09-14 | 哈尔滨工程大学 | A kind of noise reduction overflow valve based on coupling bionic principle |
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