CN118208458A - Two-gear different pressure curve adjusting method for control valve group - Google Patents
Two-gear different pressure curve adjusting method for control valve group Download PDFInfo
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- CN118208458A CN118208458A CN202410279517.2A CN202410279517A CN118208458A CN 118208458 A CN118208458 A CN 118208458A CN 202410279517 A CN202410279517 A CN 202410279517A CN 118208458 A CN118208458 A CN 118208458A
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- 230000001105 regulatory effect Effects 0.000 claims description 97
- 238000005192 partition Methods 0.000 claims description 32
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- 230000008569 process Effects 0.000 claims description 11
- 229910000831 Steel Inorganic materials 0.000 claims description 10
- 239000010959 steel Substances 0.000 claims description 10
- 239000007788 liquid Substances 0.000 claims description 8
- 230000007935 neutral effect Effects 0.000 claims description 7
- 238000007789 sealing Methods 0.000 claims description 7
- 230000003068 static effect Effects 0.000 claims description 2
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- 238000012986 modification Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 125000006850 spacer group Chemical group 0.000 description 2
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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
- 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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
Abstract
The invention relates to a two-gear different pressure curve adjusting method of a control valve bank, wherein the control valve bank comprises a pressure control valve, a two-position four-way reversing valve A, a two-position four-way reversing valve B and a sequential valve, the two-position four-way reversing valve A and the two-position four-way reversing valve B are respectively communicated with a shuttle valve, the shuttle valve is respectively connected with the two-position three-way reversing valve and the sequential valve, the two-position three-way reversing valve is respectively communicated with the pressure control valve through a throttling valve A and a throttling valve B, and the method adopts the two-position four-way reversing valves to respectively control the opening and the closing of a two-gear clutch (I, II); the p2 pressure value and the t2 time value required by the combination of the two-gear clutch are respectively controlled through the high-flow pressure control valve, the shuttle valve, the two-position three-way reversing valve, the sequence valve and the two adjustable throttle valves, so that the pressure value p2 and the time value t2 required by the gear are obtained when different gears are combined, and the impact load of each gear is reduced when the gears are combined; meets the safety and reliability requirements of special ships.
Description
Technical Field
The invention relates to a control valve group adjusting method on a medium-sized and large-sized ship and other transmission devices with wet-type hydraulic friction clutches, in particular to a two-gear different pressure curve adjusting method of a control valve group.
Background
In order to reduce the impact on the load when the clutches are combined, a specific row connecting pressure-time curve of each gear clutch is configured according to the inertia of the gear load (as shown in figure 1); when the loads of the gears are different, the pressure_time curves corresponding to the gears are different, namely the pressure p2 and the time t2 are different, and meanwhile, in order to ensure safety, the gear clutch needs to be satisfied, and can continue to work when power is lost, namely the gear clutch can not be shifted.
The method for configuring different gear pressure-time curves can use a plurality of electro-hydraulic proportional pressure reducing valves to independently control each gear clutch, but under the power-off working condition, the working condition requirements cannot be met, and the method cannot be used on special ships; and the hydraulic control system can also be realized by adopting a plurality of pressure regulating valve combinations, but a plurality of oil pumps are correspondingly configured, so that the equipment cost and the complexity of the control system are greatly increased, and the working reliability of the system is reduced.
Disclosure of Invention
In order to solve the technical problems, the invention aims to provide a two-gear different pressure curve adjusting method of a control valve group, which can realize different boost curve control requirements and special gear shifting functions when all gears of clutches are combined.
In order to achieve the above object, the present invention adopts the following technical scheme:
The two-gear different pressure curve adjusting method of the control valve bank comprises a pressure control valve, a two-position four-way reversing valve A, a two-position four-way reversing valve B and a sequence valve, wherein a plurality of chambers are arranged in the pressure control valve, the chambers comprise a pressure adjusting chamber B and a pressure adjusting chamber D, the pressure adjusting chamber B is communicated with an oil inlet, one oil outlet of the pressure control valve is respectively communicated with oil inlets of the two-position four-way reversing valve A and the two-position four-way reversing valve B, and the two-position four-way reversing valve A and the two-position four-way reversing valve B respectively control the opening and the closing of a clutch I and a clutch II; the two-position four-way reversing valve A and the two-position four-way reversing valve B are respectively communicated with a shuttle valve, the shuttle valve is respectively connected with the two-position three-way reversing valve and a sequence valve, two oil outlets of the two-position three-way reversing valve are respectively communicated with a pressure regulation cavity D of the pressure control valve through a throttle valve A and a throttle valve B, the sequence valve is also communicated with the pressure regulation cavity D of the pressure control valve, the pressure control valve comprises a valve body, a rear cover plate and a front cover plate which are fixed at two ends of the valve body, a partition plate is further clamped between the rear cover plate and the valve body, a piston and a plunger are arranged in the valve body, the cross section area of the plunger is larger than that of the piston, a large spring and a small spring are arranged in parallel between the piston and the plunger, a pressure regulation cavity A is formed between the end part of the piston, the front cover plate and the inner wall of the valve body, a throttle screw plug is further arranged on the piston, the throttle plug is communicated with the pressure regulation cavity A and the pressure regulation cavity B, a pressure regulation cavity D is formed between the plunger, the partition plate, the throttle valve B and the inner wall are respectively communicated with the partition plate and the pressure regulation cavity D; a pressure regulating C cavity is further arranged between the side wall of the piston and the inner wall of the valve body, the pressure regulating C cavity is positioned on the right side of the pressure regulating B cavity, and the pressure regulating C cavity is communicated with the oil outlet;
The adjusting method comprises the combination working condition of the clutch I and the combination working condition of the clutch II:
1. Clutch I engaged condition: at the moment, the P2 port of the two-position four-way reversing valve A is cut off, an oil inlet channel of the clutch II is communicated with an oil return port T of the two-position four-way reversing valve A, and the clutch II is depressurized and is in a discharging state; the oil liquid enters a clutch I and a pressure regulating cavity B of a pressure control valve respectively in two paths; after the oil entering the clutch I passes through the shuttle valve, one part of the oil enters a pressure regulating cavity D of the pressure control valve through a two-position three-way valve and a throttle valve B, and the other part of the oil is communicated with the pressure regulating cavity D of the pressure control valve through a sequence valve;
the oil entering the pressure regulating cavity B of the pressure control valve enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises and pushes the piston to move right, the large spring and the small spring are compressed, and part of the oil is discharged from the pressure regulating cavity C; the oil entering the pressure regulating cavity D pushes the plunger to move left, and the plunger further compresses the big spring and the small spring in the process of moving left, so that the oil pressure at the pressure regulating cavity B is gradually increased to a high-pressure state;
In the initial stage of clutch boosting, the sequence valve is in a cut-off state, when the clutch pressure is gradually increased to a set p2 value, the sequence valve is opened, oil rapidly enters a pressure regulation D cavity of the pressure control valve, under the combined action of the oil passing through the throttle valve B, the plunger rapidly moves, the oil pressure rapidly increases to a p3 value, the whole boosting process is completed, and finally a pressure_time curve required by the combination of the clutch I is obtained under the combined action of the throttle valve B and the sequence valve;
2. Clutch II engaged condition: at the moment, the P1 port of the two-position four-way reversing valve B is cut off, an oil inlet channel of the clutch I is communicated with the oil return port T of the valve body, and the clutch I is depressurized and is in a discharging state; the oil liquid enters a pressure regulating cavity B of a clutch II and a pressure control valve respectively in two paths; after the oil entering the clutch II passes through the shuttle valve, one part of the oil enters a pressure regulating cavity D of the pressure control valve through a two-position three-way valve and a throttle valve A, and the other part of the oil enters the pressure regulating cavity D of the pressure control valve through a sequence valve;
the oil entering the pressure regulating cavity B of the pressure control valve enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises and pushes the piston to move right, the large spring and the small spring are compressed, and part of the oil is discharged from the pressure regulating cavity C; the oil entering the pressure regulating cavity D pushes the plunger to move left, and the plunger further compresses the big spring and the small spring in the process of moving left, so that the oil pressure at the pressure regulating cavity B is gradually increased to a high-pressure state;
In the initial stage of clutch boosting, the sequence valve is in a cut-off state, when the clutch pressure is gradually increased to a set p2 value, the sequence valve is opened, oil rapidly enters a pressure regulation D cavity of the pressure control valve, under the combined action of the oil passing through the throttle valve B, the plunger rapidly moves, the oil pressure rapidly increases to a p3 value, the whole boosting process is completed, and finally a pressure_time curve required by the combination of the clutch II is obtained under the combined action of the throttle valve A and the sequence valve.
As a preferable scheme: an oil duct E is further arranged in the valve body, one end of the oil duct E is respectively communicated with the P2 and P1 ports of the two-position four-way reversing valve A and the two-position four-way reversing valve B, and the other end of the oil duct E is communicated with the pressure regulating cavity B; the adjustment method further includes neutral position conditions: at the moment, the P2 and P1 ports of the two-position four-way reversing valve A and the two-position four-way reversing valve B are blocked, the oil inlet channels of the clutch I and the clutch II are communicated with the oil return port T of the valve body, the clutch is depressurized, and the clutch I, II is in a discharging state; after the oil in the pressure regulating cavity B of the pressure control valve enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises to push the piston to move right and compress the big spring and the small spring, part of the oil is discharged from the pressure regulating cavity C, and the other part of the oil enters the P2 and P1 ports of the two-position four-way reversing valve A and the two-position four-way reversing valve B through the oil duct E, and the P2 and P1 ports are in a cut-off state, so that the oil in the pressure regulating cavity D of the pressure control valve is fed with oil-free liquid, the plunger is static, and the pressure regulating cavity B is in a low-pressure state.
As a preferable scheme: the pressure regulating cavity D of the pressure control valve is also connected to a shuttle valve through a one-way valve, and the shuttle valve is communicated with a port T of the two-position four-way reversing valve A or the two-position four-way reversing valve B for pressure relief; the adjusting method further comprises the following working conditions of clutch I or clutch II in a disengaging mode:
When the clutch I or the clutch II is subjected to the discharging operation, the one-way valve is opened, oil in the pressure regulating cavity D of the pressure control valve rapidly passes through the one-way valve, the shuttle valve, the two-position four-way reversing valve B or the two-position four-way reversing valve A to be communicated with the port T for pressure relief, the pressure in the pressure regulating cavity D returns to zero, the control valve returns to the neutral working condition, and the system is in a low-pressure state.
As a preferable scheme: and a pressure regulating F cavity is formed between the piston and the plunger and the inner wall of the valve body, and the T ports of the two-position four-way reversing valve A and the two-position four-way reversing valve B are communicated with the pressure regulating F cavity.
As a preferable scheme: the structure of the throttle valve A is the same as that of the throttle valve B, the throttle valve A comprises a throttle screw, a tightening nut and a screw seat, the screw seat is connected with the partition board through external threads and the throttle screw through internal threads, and the throttle screw is screwed in or screwed out to enable the flow of a corresponding flow channel communicated with the pressure regulating cavity D on the partition board to change side, and the tightening nut is further arranged at one end of the throttle screw.
As a preferable scheme: one end of the screw seat is also provided with an oil sealing nut, and a sealing gasket is also arranged between the screw seat and the partition plate.
As a preferable scheme: the one-way valve comprises a steel ball and a spring which are arranged in the partition plate, and a screw plug A connected with the partition plate, wherein two ends of the spring are respectively propped against the steel ball and the screw plug A, and the steel ball compresses a corresponding flow passage communicated with the pressure regulating D cavity under the action of the spring.
As a preferable scheme: the sequence valve comprises a valve core, a pressure spring and a plug screw B, wherein the valve core is arranged in a corresponding flow channel communicated with the pressure adjusting cavity D in the partition board, the plug screw B is connected with the partition board through threads, two ends of the pressure spring are respectively propped against the valve core and the plug screw B, and a pressure adjusting pad is further arranged between the valve core and the pressure spring.
As a preferable scheme: the two-position four-way reversing valve A and the two-position four-way reversing valve B are arranged at the top of the pressure control valve in parallel, and the two-position four-way reversing valve A and the two-position four-way reversing valve B are all electric control reversing valves with valve core positioning and mechanical emergency functions.
As a preferable scheme: the two-position three-way valve is an inserted electromagnetic reversing valve with a mechanical emergency function and is arranged in the rear cover plate.
Compared with the prior art, the invention has the beneficial effects that:
The method adopts two-position four-way reversing valves to respectively control the opening and closing of a two-gear clutch (I, II); the p2 pressure value and the t2 time value required by the combination of the two-gear clutch are respectively controlled through the high-flow pressure control valve, the shuttle valve, the two-position three-way reversing valve, the sequence valve and the two adjustable throttle valves, so that the pressure value p2 and the time value t2 required by the gear are obtained when different gears are combined, and the impact load of each gear is reduced when the gears are combined; meets the safety and reliability requirements of special ships.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application.
FIG. 1 is a gear pressure graph of the present invention;
FIG. 2 is a schematic diagram of the hydraulic principle of the present invention;
FIG. 3 is a schematic top view of a control valve block of the present invention;
FIG. 4 is a schematic end view of a control valve block of the present invention;
FIG. 5 is a cross-sectional view of C-C of FIG. 4;
FIG. 6 is a schematic side view of a control valve block of the present invention;
fig. 7 is a D-D cross-sectional view of fig. 6.
The reference numerals are: 1. a pressure control valve; 101. a piston; 102. a throttle screw plug; 103. a valve body; 104. a large spring; 105. a small spring; 106. a plunger; 107. a positioning ring; 108. a partition plate; 109. a back cover plate; 110. a front cover plate;
2. A two-position four-way reversing valve A; 3. a two-position four-way reversing valve B; 4. a shuttle valve; 5. a two-position three-way reversing valve; 6. a throttle valve A; 601. an oil seal nut; 602. a throttle screw; 603. tightening the nut; 604. a screw seat; 605. a sealing gasket; 7. a throttle valve B; 8. a one-way valve; 801. a steel ball; 802. a spring; 803. a screw plug A; 804. a gasket; 9. a sequence valve; 901. a valve core; 902. a pressure spring; 903. a sealing gasket; 904. a screw plug B; 905. and a pressure adjusting pad.
Detailed Description
It should be noted that the following detailed description is illustrative and is intended to provide further explanation of the application. 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 application belongs.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
Furthermore, in the description of the present invention, it should be understood that the terms "center," "longitudinal," "transverse," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "clockwise," "counterclockwise," etc. indicate or are based on the orientation or positional relationship shown in the drawings, merely for convenience of description and to simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the invention.
Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present invention, unless otherwise specified, the meaning of "a plurality" is two or more, unless otherwise clearly defined.
In the present invention, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
In the present invention, unless expressly stated or limited otherwise, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, as well as the first and second features not being in direct contact but being in contact with each other through additional features therebetween. Moreover, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicating that the first feature is higher in level than the second feature. The first feature being "under", "below" and "beneath" the second feature includes the first feature being directly under and obliquely below the second feature, or simply means that the first feature is less level than the second feature.
The invention is further illustrated by the following examples in conjunction with the accompanying drawings:
As shown in fig. 2 to 7, a control valve group capable of realizing two-gear pressure regulation comprises a pressure control valve 1, a two-position four-way reversing valve A2, a two-position four-way reversing valve B3 and a sequence valve 9, wherein the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 are arranged at the top of the pressure control valve 1 in parallel, the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 are all electric control reversing valves with valve core positioning and mechanical emergency functions, a plurality of chambers are arranged in the pressure control valve 1, each chamber comprises a pressure regulation cavity B and a pressure regulation cavity D, the pressure regulation cavity is communicated with an oil inlet, one oil outlet of the pressure control valve 1 is respectively communicated with oil inlets of the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3, and the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 respectively control the opening and closing of a clutch I and a clutch II; and the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 are respectively communicated with the shuttle valve 4, the shuttle valve 4 is respectively connected with the two-position three-way reversing valve 5 and the sequence valve 9, two oil outlets of the two-position three-way reversing valve 5 are respectively communicated with the pressure regulation D cavity of the pressure control valve 1 through the throttle valve A6 and the throttle valve B7, and the sequence valve 9 is also communicated with the pressure regulation D cavity of the pressure control valve 1. The pressure regulation D cavity of the pressure control valve 1 is also connected to the shuttle valve 4 through a one-way valve 8, and the shuttle valve 4 is communicated with the T port of the two-position four-way reversing valve A2 or the two-position four-way reversing valve B3 for pressure relief.
As shown in fig. 5, the pressure control valve 1 includes a valve body 103, and a rear cover plate 109 and a front cover plate 110 fixed at two ends of the valve body 103, the two-position three-way valve 5 is a plug-in electromagnetic directional valve with a mechanical emergency function, and is disposed in the rear cover plate 109, a partition plate 108 is further sandwiched between the rear cover plate 109 and the valve body 103, and a positioning ring 107 is further disposed between the partition plate 108 and the valve body 103. A piston 101 and a plunger 106 are arranged in the valve body 103, and the cross section area of the plunger 106 is larger than that of the piston 101. The piston 101 and the plunger 106 respectively form small clearance fit with an inner hole of the valve body 103, a large spring 104 and a small spring 105 are arranged between the piston 101 and the plunger 106 in parallel, a pressure adjusting A cavity is formed among the end part of the piston 101, a front cover plate 110 and the inner wall of the valve body 103, a pressure adjusting B cavity is formed among the side wall of the piston 101 and the inner wall of the valve body 103, a throttle screw plug 102 is further arranged on the piston 101, the throttle screw plug 102 is communicated with the pressure adjusting A cavity and the pressure adjusting B cavity, a pressure adjusting D cavity is formed among the plunger 106, a partition plate 108 and the inner wall of the valve body 103, and a throttle valve A6, a throttle valve B7, a one-way valve 8 and a sequence valve 9 are all arranged on the partition plate 108 and are communicated with the pressure adjusting D cavity.
A pressure regulating C cavity is further arranged between the side wall of the piston 101 and the inner wall of the valve body 103, the pressure regulating C cavity is positioned on the right side of the pressure regulating B cavity, and the pressure regulating C cavity is communicated with the oil outlet. An oil duct E is further arranged in the valve body 103, one end of the oil duct E is respectively communicated with the P2 and P1 ports of the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3, and the other end of the oil duct E is communicated with the pressure regulating cavity B. And a pressure regulating F cavity is formed between the piston 101 and the plunger 106 and the inner wall of the valve body 103, and the T ports of the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 are communicated with the pressure regulating F cavity.
As shown in fig. 7, the structure of the throttle valve A6 is the same as that of the throttle valve B7, the throttle valve A6 includes a throttle screw 602, a tightening nut 603 and a screw seat 604, the screw seat 604 is connected with the partition board 108 through an external thread, is connected with the throttle screw 602 through an internal thread, and is screwed in or screwed out of the throttle screw 602, so that the flow of the corresponding flow channel on the partition board 108, which is communicated with the pressure adjusting D cavity, is changed by edge, one end of the throttle screw 602 is further provided with the tightening nut 603, and the setting of the tightening nut 603 can be locked after the adjustment of the throttle screw 602 is finished, so as to prevent the throttle screw 602 from loosening. An oil seal nut 601 is further arranged at one end of the screw seat 604, and a sealing gasket 605 is further arranged between the screw seat 604 and the partition plate 108.
The one-way valve 8 comprises a steel ball 801 and a spring 802 which are arranged in the partition plate 108, and a screw plug A803 connected with the partition plate 108, wherein two ends of the spring 802 are respectively abutted against the steel ball 801 and the screw plug A803, and the steel ball 801 compresses corresponding flow channels communicated with the pressure adjusting D cavity under the action of the spring 802. A gasket 804 is also provided between the plug a803 and the spacer 108.
The sequence valve 9 comprises a valve core 901, a pressure spring 902 and a plug screw B904, wherein the valve core 901 is arranged in a corresponding flow passage communicated with a pressure regulation D cavity in the partition plate 108, and an outer circle at one end of the valve core 901 is in small clearance fit with an inner hole of the partition plate 108. The plug screw B904 is connected with the partition plate 108 through threads, two ends of the pressure spring 902 are respectively abutted against the valve core 901 and the plug screw B904, a pressure adjusting pad 905 is further arranged between the valve core 901 and the pressure spring 902, the opening pressure of the sequence valve is set to be a p2 value required in a pressure_time curve, and the opening pressure of the sequence valve can be set through the pressure adjusting pad 905. A gasket 903 is also provided between the plug B904 and the spacer 108.
A two-gear different pressure curve adjusting method of a control valve bank includes the following steps of respectively describing the working process of the valve bank from four working conditions of the valve bank, namely a neutral working condition, a clutch I combining working condition, a clutch II combining working condition and a clutch I (or clutch II) discharging working condition:
1. Neutral position operating mode: at the moment, the YV1 of the two-position four-way reversing valve A2 and the YV3 of the two-position four-way reversing valve B3 are powered on, the P2 and P1 ports of the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 are blocked, the oil inlet channels of the clutch I and the clutch II are communicated with the oil return port T of the valve body, the clutch is depressurized, and the clutch I, II is in a discharging state; after the oil in the pressure regulating cavity B of the pressure control valve 1 enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises to push the piston 101 to move right and compress the large spring 104 and the small spring 105, part of the oil is discharged from the pressure regulating cavity C, and the other part of the oil enters the ports P2 and P1 of the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 through the oil duct E, and the ports P2 and P1 are in a cut-off state, so that the oil in the pressure regulating cavity D of the pressure control valve 1 is fed without displacement, and the pressure regulating cavity B is in a low-pressure state.
2. Clutch I engaged condition: at the moment, YV1 of the two-position four-way reversing valve A2 and YV4 of the two-position four-way reversing valve B3 are powered (or pulse current is fed), other electromagnets are not powered, the P2 port of the two-position four-way reversing valve A2 is cut off, an oil inlet channel of the clutch II is communicated with an oil return port T of the valve body, and the clutch II is depressurized and is in a discharging state. The oil liquid enters a clutch I and a pressure regulating cavity B of a pressure control valve 1 respectively in two ways; after the oil entering the clutch I passes through the shuttle valve 4, one part of the oil enters the pressure regulating cavity D of the pressure control valve 1 through the two-position three-way valve 5 and the throttle valve B7, and the other part of the oil is communicated with the pressure regulating cavity D of the pressure control valve 1 through the sequence valve 9.
After entering the pressure regulating cavity B of the pressure control valve 1 and entering the pressure regulating cavity A through the inner oil duct, the pressure gradually rises and pushes the piston 101 to move right, compressing the large spring 104 and the small spring 105 and discharging part of oil from the pressure regulating cavity C; the oil entering the pressure regulating D cavity pushes the plunger 106 to move left, and the plunger 106 is continuously moved left along with the increase of the oil inlet amount of the pressure regulating D cavity until being limited by the step of the inner hole of the valve body 103 because the sectional area of the plunger 106 is larger than that of the piston 101. During the left movement of the plunger 106, the large spring 104 and the small spring 105 are further compressed, so that the oil pressure at the pressure regulation B chamber is gradually increased to a high pressure state.
The pressure of the pressure control valve 1 adjusts the oil pressure of the B chamber by adjusting the opening size of the throttle valve B7, and the pressure-adjusting time t2 of the oil pressure of the B chamber (i.e., the working oil pressure) is adjusted by adjusting the opening size of the throttle valve B7, because the oil pressure increasing time of the B chamber depends on the speed at which the plunger 106 moves to the left and the speed at which the plunger 106 moves to the left depends on the flow rate of the oil passing through the throttle valve B7.
In the initial stage of clutch boosting, the sequence valve 9 is in a cut-off state, when the clutch pressure gradually rises to a set p2 value, the sequence valve 9 is opened, oil rapidly enters a pressure adjusting cavity D of the pressure control valve 1, the plunger 106 rapidly moves under the combined action of the oil and the oil passing through the throttle valve B7, the oil pressure also rapidly rises to a p3 value, and the whole boosting process is completed. Finally, under the combined action of throttle valve B7 and sequential valve 9, the pressure-time curve required for the engagement of clutch I is obtained.
3. Clutch II engaged condition: at this time
The YV2 of the two-position four-way reversing valve A2, the YV2 of the two-position four-way reversing valve B3 and the YV5 of the two-position three-way valve 5 are powered (or pulse current is fed), other electromagnets are not powered, the P1 port of the two-position four-way reversing valve B3 is cut off, an oil inlet channel of the clutch I is communicated with an oil return port T of the valve body, and the clutch I is depressurized and is in a discharging state. The oil liquid enters a pressure regulating cavity B of the clutch II and the pressure control valve 1 respectively in two paths; after the oil entering the clutch II passes through the shuttle valve 4, one part of the oil enters the pressure regulating cavity D of the pressure control valve 1 through the two-position three-way valve 5 and the throttle valve A6, and the other part of the oil enters the pressure regulating cavity D of the pressure control valve 1 through the sequence valve 9.
Similarly, after the oil entering the pressure regulating cavity B of the pressure control valve 1 enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises and pushes the piston 101 to move right, compressing the large spring 104 and the small spring 105, and discharging part of the oil from the pressure regulating cavity C; the oil entering the pressure regulating D chamber of the pressure control valve 1 pushes the plunger 106 to move left, and since the cross-sectional area of the plunger 106 is larger than that of the piston 101, the plunger continuously moves left with the increase of the oil inlet amount of the pressure regulating D chamber until being limited by the step of the inner hole of the valve body 103. During the left movement of the plunger 106, the large spring 104 and the small spring 105 are further compressed, so that the oil pressure at the pressure regulation B chamber is gradually increased to a high pressure state.
The pressure of the pressure control valve 1 adjusts the oil pressure of the B chamber by adjusting the opening size of the throttle valve A6, and the pressure-increasing time t2 of the oil pressure of the B chamber (i.e., the working oil pressure) is adjusted by adjusting the opening size of the throttle valve A6, because the oil pressure increasing time of the B chamber depends on the speed of the plunger 106 moving to the left and the speed of the plunger 106 moving to the left depends on the flow rate of the oil passing through the relief valve A6.
In the initial stage of clutch boosting, the sequence valve 9 is in a cut-off state, when the clutch pressure gradually rises to a set p2 value, the sequence valve 9 is opened, oil rapidly enters a pressure adjusting cavity D of the pressure control valve 1, the plunger 106 rapidly moves under the combined action of the oil and the oil passing through the throttle valve A6, the oil pressure rapidly rises to a p3 value, and the whole boosting process is completed. Finally, the pressure-time curve required for the coupling of clutch II is obtained by the combined action of throttle valve 6 and sequence valve 9.
4. Clutch I (or clutch II) de-exhaust condition
When the clutch I (or the clutch II) is subjected to the discharging operation, the one-way valve 8 is opened, oil in the pressure regulating D cavity of the pressure control valve 1 is quickly discharged through the T port communicated with the one-way valve 8, the shuttle valve 4 and the two-position four-way reversing valve B3 (or the two-position four-way reversing valve A2), the pressure in the pressure regulating D cavity returns to zero, the control valve returns to the neutral working condition, and the system is in a low-pressure state. The quick oil return of the one-way valve 8 can enable the clutch to be rapidly released, and the risks of high temperature and sheet burning of the clutch are prevented.
When the clutch does not work, the control valve group of the invention can always increase the pressure of the system to the set value only when the clutch of a certain gear is combined in the low-pressure state of the system, thereby reducing the energy loss of the prime motor.
The invention adopts a high-flow pressure control valve 1, a two-position four-way reversing valve A2 and a two-position four-way reversing valve B3 to respectively control the opening and closing of a two-gear clutch (I, II); the shuttle valve 4, the two-position three-way reversing valve 5, the one-way valve 8, the sequence valve 9, the adjustable throttle valve A6 and the adjustable throttle valve B7 are used for respectively controlling a p2 pressure value and a t2 time value required by the combination of two-gear clutches, so that the pressure value p2 and the time value t2 required by the gear are obtained when different gears are combined, and the impact load of each gear is reduced; when the power is lost, the two-position four-way reversing valve A2 and the two-position four-way reversing valve B3 have power-loss protection (namely, when the electromagnetic valve is powered off, the original gear is kept unchanged) and mechanical emergency functions, and the two-position three-way valve 5 has a mechanical emergency mechanism, so that the safety and reliability requirements of special ships are met. The invention adopts an integrated design, combines all parts together through the internal oil way, reduces the weight of the assembly, and improves the working reliability and maintainability.
In the description of the present specification, a description referring to terms "one embodiment," "some embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
Although embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives and variations may be made to the above embodiments by those skilled in the art without departing from the spirit and principles of the invention, and any simple modification, equivalent variation and modification of the above embodiments in light of the technical principles of the invention may be made within the scope of the present invention.
Claims (10)
1. A two-gear different pressure curve adjusting method of a control valve group is characterized by comprising the following steps of: the control valve group comprises a pressure control valve (1), a two-position four-way reversing valve A (2), a two-position four-way reversing valve B (3) and a sequence valve (9), wherein a plurality of chambers are arranged in the pressure control valve (1), the chambers comprise a pressure regulation B chamber and a pressure regulation D chamber, the pressure regulation B chamber is communicated with an oil inlet, one oil outlet of the pressure control valve (1) is respectively communicated with oil inlets of the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3), and the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3) respectively control the opening and closing of a clutch I and a clutch II; and two-position four-way reversing valve A (2), two-position four-way reversing valve B (3) are respectively communicated with shuttle valve (4), shuttle valve (4) are respectively connected two-position three-way reversing valve (5) and sequence valve (9), two oil outlets of two-position three-way reversing valve (5) are respectively communicated with pressure regulating D cavity of pressure control valve (1) through throttle valve A (6), throttle valve B (7), sequence valve (9) are also communicated with pressure regulating D cavity of pressure control valve (1), pressure control valve (1) includes valve body (103) and back cover plate (109) and front cover plate (110) fixed at both ends of valve body (103), baffle plate (108) is still inserted between back cover plate (109) and valve body (103), piston (101) and plunger (106) are arranged in valve body (103), the sectional area of plunger (106) is greater than that of piston (101), big spring (104) and small spring (105) are parallelly connected between piston (101) and plunger (106), end part of piston (101) and front cover plate (103) and inner wall (103) form between pressure regulating piston (101) and valve body (103) and inner wall (101), the throttle screw plug (102) is communicated with the pressure regulation A cavity and the pressure regulation B cavity, a pressure regulation D cavity is formed among the plunger (106), the partition plate (108) and the inner wall of the valve body (103), and the throttle valve A (6), the throttle valve B (7), the one-way valve (8) and the sequence valve (9) are all arranged on the partition plate (108) and are all communicated with the pressure regulation D cavity; a pressure regulating C cavity is further arranged between the side wall of the piston (101) and the inner wall of the valve body (103), the pressure regulating C cavity is positioned on the right side of the pressure regulating B cavity, and the pressure regulating C cavity is communicated with the oil outlet;
The adjusting method comprises the combination working condition of the clutch I and the combination working condition of the clutch II:
1. Clutch I engaged condition: at the moment, the P2 port of the two-position four-way reversing valve A (2) is cut off, an oil inlet channel of the clutch II is communicated with an oil return port T of the two-position four-way reversing valve A (2), and the clutch II is depressurized and is in a discharging state; the oil liquid enters a clutch I and a pressure regulating cavity B of a pressure control valve (1) respectively in two ways; after the oil entering the clutch I passes through the shuttle valve (4), one part of the oil enters a pressure regulating cavity D of the pressure control valve (1) through a two-position three-way valve (5) and a throttle valve B (7), and the other part of the oil is communicated with the pressure regulating cavity D of the pressure control valve (1) through a sequence valve (9);
The oil entering the pressure regulating cavity B of the pressure control valve (1) enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises and pushes the piston (101) to move right, the large spring (104) and the small spring (105) are compressed, and part of the oil is discharged from the pressure regulating cavity C; the oil entering the pressure regulating cavity D pushes the plunger (106) to move left, and the plunger (106) further compresses the large spring (104) and the small spring (105) in the process of moving left, so that the oil pressure at the pressure regulating cavity B is gradually increased to a high-pressure state;
In the initial stage of clutch boosting, the sequence valve (9) is in a cut-off state, when the clutch pressure is gradually increased to a set p2 value, the sequence valve (9) is opened, oil rapidly enters a pressure regulating cavity D of the pressure control valve (1), under the combined action of the oil and the oil passing through the throttle valve B (7), the plunger (106) rapidly moves, the oil pressure also rapidly increases to a p3 value, the whole boosting process is completed, and finally, a pressure_time curve required by the combination of the clutch I is obtained under the combined action of the throttle valve B (7) and the sequence valve (9);
2. clutch II engaged condition: at the moment, the P1 port of the two-position four-way reversing valve B (3) is cut off, an oil inlet channel of the clutch I is communicated with the oil return port T of the valve body, and the clutch I is decompressed and is in a discharging state; the oil liquid enters a clutch II and a pressure regulating cavity B of a pressure control valve (1) respectively in two ways; after the oil entering the clutch II passes through the shuttle valve (4), one part of the oil enters a pressure regulating cavity D of the pressure control valve (1) through a two-position three-way valve (5) and a throttle valve A (6), and the other part of the oil enters the pressure regulating cavity D of the pressure control valve (1) through a sequence valve (9);
The oil entering the pressure regulating cavity B of the pressure control valve (1) enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises and pushes the piston (101) to move right, the large spring (104) and the small spring (105) are compressed, and part of the oil is discharged from the pressure regulating cavity C; the oil entering the pressure regulating cavity D pushes the plunger (106) to move left, and the plunger (106) further compresses the large spring (104) and the small spring (105) in the process of moving left, so that the oil pressure at the pressure regulating cavity B is gradually increased to a high-pressure state;
In the initial stage of clutch boosting, the sequence valve (9) is in a cut-off state, when the clutch pressure is gradually increased to a set p2 value, the sequence valve (9) is opened, oil rapidly enters a pressure adjusting D cavity of the pressure control valve (1), under the combined action of the oil and the oil passing through the throttle valve B (7), the plunger (106) rapidly moves, the oil pressure also rapidly increases to a p3 value, the whole boosting process is completed, and finally, a pressure_time curve required by the combination of the clutch II is obtained under the combined action of the throttle valve A (6) and the sequence valve (9).
2. The method for adjusting the two-gear different pressure curve of the control valve group according to claim 1, wherein the method comprises the following steps: an oil duct E is further arranged in the valve body (103), one end of the oil duct E is respectively communicated with the P2 and P1 ports of the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3), and the other end of the oil duct E is communicated with the pressure regulating cavity B; the adjusting step further includes neutral operating conditions: at the moment, the P2 and P1 ports of the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3) are blocked, the oil inlet channels of the clutch I and the clutch II are communicated with the oil return port T of the valve body, the clutch is depressurized, and the clutch I, II is in a discharge state; after the oil in the pressure regulating cavity B of the pressure control valve (1) enters the pressure regulating cavity A through the inner oil duct, the pressure gradually rises to push the piston (101) to move right and compress the large spring (104) and the small spring (105), part of the oil is discharged from the pressure regulating cavity C, the other part of the oil enters the ports P2 and P1 of the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3) through the oil duct E, and the ports P2 and P1 are in a cut-off state, oil-free liquid in the pressure regulating cavity D of the pressure control valve (1) enters, the plunger (106) is static, and the pressure regulating cavity B is in a low-pressure state.
3. The method for adjusting the two-gear different pressure curve of the control valve group according to claim 1, wherein the method comprises the following steps: the pressure regulating cavity D of the pressure control valve (1) is also connected to the shuttle valve (4) through a one-way valve (8), and the shuttle valve (4) is communicated with the port T of the two-position four-way reversing valve A (2) or the two-position four-way reversing valve B (3) for pressure relief; the adjusting step further comprises the working condition of clutch I or clutch II in a disengagement mode:
When the clutch I or the clutch II is subjected to the discharging operation, the one-way valve (8) is opened, oil in the pressure regulating cavity D of the pressure control valve (1) rapidly passes through the one-way valve (8), the shuttle valve (4), the two-position four-way reversing valve B (3) or the two-position four-way reversing valve A (2) to be communicated with the port T for pressure relief, the pressure in the pressure regulating cavity D returns to zero, the control valve returns to the neutral working condition, and the system is in a low-pressure state.
4. The control valve group capable of realizing two-gear pressure adjustment according to claim 1, wherein: the piston (101) and the plunger (106) form a pressure adjusting F cavity with the inner wall of the valve body (103), and the T ports of the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3) are communicated with the pressure adjusting F cavity.
5. The control valve group capable of realizing two-gear pressure adjustment according to claim 1, wherein: the throttle valve A (6) and the throttle valve B (7) are identical in structure, the throttle valve A (6) comprises a throttle screw (602), a tightening nut (603) and a screw seat (604), the screw seat (604) is connected with the partition board (108) through external threads and the throttle screw (602) through internal threads, and the throttle screw (602) is screwed in or screwed out, so that the flow of a corresponding flow channel communicated with the pressure adjusting cavity D on the partition board (108) is changed in edge, and one end of the throttle screw (602) is further provided with the tightening nut (603).
6. The control valve group capable of realizing two-gear pressure adjustment according to claim 5, wherein: one end of the screw seat (604) is also provided with an oil sealing nut (601), and a sealing gasket (605) is also arranged between the screw seat (604) and the partition plate (108).
7. The control valve group capable of realizing two-gear pressure adjustment according to claim 1, wherein: the one-way valve (8) comprises a steel ball (801) and a spring (802) which are arranged in the partition plate (108), and a screw plug A (803) connected with the partition plate (108), wherein two ends of the spring (802) are respectively propped against the steel ball (801) and the screw plug A (803), and the steel ball (801) compresses corresponding flow channels communicated with the pressure adjusting D cavity under the action of the spring (802).
8. The control valve group capable of realizing two-gear pressure adjustment according to claim 1, wherein: the sequence valve (9) comprises a valve core (901), a pressure spring (902) and a screw plug B (904), wherein the valve core (901) is arranged in a corresponding flow passage communicated with a pressure regulation cavity D in a partition plate (108), the screw plug B (904) is connected with the partition plate (108) through threads, two ends of the pressure spring (902) respectively prop against the valve core (901) and the screw plug B (904), and a pressure regulation pad (905) is further arranged between the valve core (901) and the pressure spring (902).
9. The control valve group capable of realizing two-gear pressure adjustment according to claim 1, wherein: the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3) are arranged at the top of the pressure control valve (1) in parallel, and the two-position four-way reversing valve A (2) and the two-position four-way reversing valve B (3) are all electric control reversing valves with valve core positioning and mechanical emergency functions.
10. The control valve group capable of realizing two-gear pressure adjustment according to claim 1, wherein: the two-position three-way valve (5) is a plug-in type electromagnetic reversing valve with a mechanical emergency function and is arranged in the rear cover plate (109).
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| CN202410279517.2A CN118208458A (en) | 2024-03-12 | 2024-03-12 | Two-gear different pressure curve adjusting method for control valve group |
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| CN202410279517.2A CN118208458A (en) | 2024-03-12 | 2024-03-12 | Two-gear different pressure curve adjusting method for control valve group |
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| DE102017130297A1 (en) * | 2017-12-18 | 2019-06-19 | Schaeffler Technologies AG & Co. KG | actuator |
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| CN117028561A (en) * | 2023-08-24 | 2023-11-10 | 杭州前进齿轮箱集团股份有限公司 | Pressure regulating method of mechanical gear shifting valve |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102359586A (en) * | 2011-11-10 | 2012-02-22 | 安徽合力股份有限公司 | Proportional voltage regulation control system for automatic gearbox of forklift truck |
| CN103075509A (en) * | 2013-01-30 | 2013-05-01 | 江苏柳工机械有限公司 | Power gear shift speed change operating valve with independent buffer for gears |
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