CN112049828B - Secondary flow distribution device and load sensitive flow distribution mechanism - Google Patents
Secondary flow distribution device and load sensitive flow distribution mechanism Download PDFInfo
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- CN112049828B CN112049828B CN202010831551.8A CN202010831551A CN112049828B CN 112049828 B CN112049828 B CN 112049828B CN 202010831551 A CN202010831551 A CN 202010831551A CN 112049828 B CN112049828 B CN 112049828B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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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
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Abstract
The invention belongs to the field of hydraulic equipment, and particularly relates to a secondary flow distribution device and a load-sensitive flow distribution mechanism. Because the position switching of the plurality of rhombic through holes and the plurality of oil outlet triangular windows and/or the plurality of oil return triangular serial ports realizes the on-off of the outer oil inlet cavity and the inner oil outlet cavity and/or the inner oil return cavity, when the rotation speed of the flow distribution shaft is high, the switching frequency of the valve port is high, the flow area of the valve port is large, and when the oil inlet is communicated with the oil outlet, the pressure of the oil inlet is similar to the pressure of the oil outlet; on the contrary, when the oil inlet is communicated with the oil return port, the pressure of the oil inlet is similar to the pressure of the oil return port. The flow of the oil outlet is the flow required by the system work, and the flow of the oil return port is the redundant flow which is not compressed and output by the hydraulic pump. Because the redundant oil that the oil return opening flows out does not pass through the hydraulic pump and compresses into high-pressure oil, so this partial flow's oil does not have extra waste energy.
Description
Technical Field
The invention belongs to the field of hydraulic equipment, and particularly relates to a secondary flow distribution device and a load-sensitive flow distribution mechanism.
Background
The hydraulic control system is based on power provided by a motor, and converts mechanical energy into pressure potential energy and hydraulic oil kinetic energy by using a hydraulic pump. The flow direction of the hydraulic oil is changed by controlling various valves, so that the hydraulic cylinder or the hydraulic motor is pushed to perform actions with different strokes and different directions, and different action requirements of various devices are met.
The total energy in the hydraulic system is the product of the pressure and flow of the hydraulic oil converted from mechanical energy by the hydraulic pump. The system pressure in a conventional hydraulic system is set by an overflow valve, and when the flow required by the system is smaller than the output flow of a hydraulic pump, redundant flow can flow back to an oil tank from the overflow valve to keep the system pressure unchanged, which can cause the energy loss of overflowed high-pressure hydraulic oil.
In order to meet the energy-saving requirement of the system under different flow rates, two methods of changing the rotating speed of the motor and changing the displacement of the hydraulic pump are usually adopted. The method that the servo motor controls the rotating speed of the motor according to system requirements is adopted, and the control system of the servo motor is large in size and complex in algorithm, so that the hydraulic system is larger in required installation size; the adoption of the method of changing the displacement of the hydraulic pump complicates the structure of the hydraulic pump and makes the hydraulic pump more prone to malfunction or damage.
No matter the variable control of the output flow of the hydraulic pump is realized by adopting the servo motor or the variable pump, the original fixed-rotating-speed motor or the original fixed-displacement hydraulic pump is rejected, and the waste of the use cost is caused.
The traditional method for controlling the flow of a hydraulic system is to adopt a throttling or volume speed regulating circuit (directly controlling the flow and further indirectly controlling the speed). The throttling speed regulation loop is essentially a valve control system, such as a fixed displacement pump and a proportional valve system, and has the advantages of simple structure and low manufacturing cost, from the aspect of control bandwidth, compared with a variable displacement pump system, the fixed displacement pump and the proportional valve system have the advantage of high control bandwidth, because the variable displacement of the variable displacement pump is realized by changing the angle or the eccentricity of a swash plate (plunger pump), and the swash plate or an eccentric stator has certain mass, so the control bandwidth is low, but the throttling speed regulation utilizes a throttling hole to control the flow, and the throttling loss is inevitably generated. However, the volumetric speed control loop, such as a variable displacement pump system, has good adaptivity, the output pressure and flow rate of the volumetric speed control loop can be consistent with the load demand, the problems of flow rate inadaptation and pressure inadaptation of a throttling speed control system (adopting valve port throttling and overflow) are solved, the energy loss is greatly reduced, the system efficiency is improved, and the energy-saving effect is very obvious, but the volumetric speed control loop has a complex variable displacement mechanism and is generally more complex than a hydraulic valve for changing the hydraulic resistance.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide a secondary flow distribution device and a load-sensitive flow distribution mechanism.
The technical scheme adopted by the invention is as follows: a secondary flow distribution device comprises a valve body, wherein a cavity is formed in the valve body, the two ends of the cavity are respectively connected with a first end cover and a second end cover, a flow distribution shaft and a flow distribution sleeve sleeved outside the flow distribution shaft are arranged in the valve body, the two ends of the flow distribution sleeve are respectively abutted against the first end cover and the second end cover, and the flow distribution sleeve is in linkage fit with the valve body;
the outer wall of the flow distribution sleeve is sequentially provided with a first sealing ring, a second sealing ring, a third sealing ring, a fourth sealing ring and a fifth sealing ring along the axial direction, the outer walls of the first sealing ring, the second sealing ring, the third sealing ring, the fourth sealing ring and the fifth sealing ring are in sealing fit with the inner wall of the valve body, so that an outgoing oil cavity, an external oil inlet cavity, an external oil return cavity and an external controlled oil cavity which are separated from each other and sequentially arranged along the axial direction are formed between the flow distribution sleeve and the valve body, and the valve body is provided with an oil inlet communicated with the external oil inlet cavity, an oil return port communicated with the external oil return cavity and a channel communicated with the outgoing oil cavity and the external controlled oil cavity;
the outer wall of the valve shaft is sequentially provided with a first convex ring, a second convex ring and a third convex ring along the axial direction, the outer walls of the first convex ring, the second convex ring and the third convex ring are matched with the inner wall of the valve sleeve, so that an inner oil outlet cavity between the first convex ring and the second convex ring and an inner oil return cavity between the second convex ring and the third convex ring are formed between the valve shaft and the valve sleeve, an inner control cavity is formed between the side surface of one side of the first convex ring close to the first end cover and the flow distribution sleeve, the end surface of the flow distribution shaft and the first end cover, a sealing sleeve is arranged on one side of the third convex ring close to the second end cover, an inner controlled oil cavity is formed among the sealing sleeve, the third convex ring, the inner wall of the flow distribution sleeve and the outer wall of the flow distribution shaft, the flow distribution sleeve is provided with a second through hole for communicating the external oil outlet cavity with the internal oil outlet cavity, a third through hole for communicating the external oil return cavity with the internal oil return cavity, and a fourth through hole for communicating the external controlled oil cavity with the internal controlled oil cavity;
a plurality of rhombic through holes which are uniformly distributed along the circumferential direction are formed between the second sealing ring and the third sealing ring on the flow distribution sleeve, a plurality of oil outlet triangular windows which are uniformly distributed along the circumferential direction and are close to the inner oil outlet cavity and a plurality of oil return triangular windows which are close to the inner oil return cavity are formed in two ends of the second convex ring respectively, and the plurality of oil outlet triangular windows and the plurality of oil return triangular windows are arranged in a staggered mode; the number of the oil outlet triangular windows, the number of the oil return triangular windows and the number of the rhombic through holes are consistent;
a rotary driving shaft penetrates through the second end cover, the rotary driving shaft is in circumferential linkage fit with the flow distribution shaft, and the flow distribution shaft can axially slide relative to the rotary driving shaft;
the flow distribution shaft and the first end cover are provided with springs, and the springs form thrust to the flow distribution shaft;
the valve body is provided with a control oil port communicated with the inner control cavity and/or an adjusting device for controlling the compression amount of the spring;
the flow distribution shaft axially slides relative to the rotary driving shaft and is provided with a first position at which the rhombic through hole is communicated/disconnected with the inner oil outlet cavity through position switching with the oil outlet triangular window in the circumferential rotation state of the flow distribution shaft, a second position at which the rhombic through hole is alternately communicated with the inner oil outlet cavity and the inner oil return cavity through alternate position switching with the oil outlet triangular window and the oil return triangular window in the circumferential rotation state of the flow distribution shaft, and a third position at which the rhombic through hole is communicated/disconnected with the inner oil return cavity through position switching with the oil return triangular window in the circumferential rotation state of the flow distribution shaft.
The end part of the rotary driving shaft is provided with a linkage pin, two ends of the linkage pin are respectively fixed with a ball bearing, one end of the port shaft close to the second end cover is provided with a chute matched with the linkage pin and the ball bearings at the two ends, and the linkage pin and the ball bearings at the two ends are positioned in the chute to enable the rotary driving shaft and the port shaft to be in circumferential linkage and axially slide.
And a lubricating channel for communicating the sliding groove with the inner oil outlet cavity is arranged on the valve shaft.
The sealing sleeve is annular, two end faces of the sealing sleeve are planes, one end face of the sealing sleeve is abutted to the second end cover, the inner wall of the sealing sleeve is in clearance seal fit with the outer wall of the port shaft, and the outer wall of the sealing sleeve is in clearance seal fit with the inner wall of the port sleeve.
The second end cover comprises a split adapter and a cover plate, and the cover plate, the adapter and the valve body are sequentially connected through bolts; the adapter is sleeved outside the port shaft and is in clearance fit with the port shaft; two ends of the flow distribution sleeve are respectively abutted against the first end cover and the adaptor; the end face of the seal sleeve is abutted to the adaptor.
An outer control cavity is arranged between the valve body and the flow distribution sleeve, a first through hole communicated with the outer control cavity and the inner control cavity is formed in the flow distribution sleeve, a control oil port communicated with the outer control cavity is formed in the valve body, a blind hole is formed in the flow distribution shaft close to the first end cover, a spring seat is limited in the blind hole, a spring limiting groove is formed in the inner end face of the first end cover, and two ends of the spring are limited through the spring seat and the spring limiting groove respectively.
An outer control cavity is arranged between the valve body and the flow distribution sleeve, a first through hole which is communicated with the outer control cavity and the inner control cavity is arranged on the flow distribution sleeve, a control oil port which is communicated with the outer control cavity is arranged on the valve body, a spring limiting groove is arranged on the inner end face of the first end cover, the spring is limited in the spring limiting groove, a plane bearing is arranged between the spring and the end face of the flow distribution shaft, and a gap is formed between the outer wall of the plane bearing and the inner wall of the spring limiting groove; the spring remains in a contracted state.
The first end cover is connected with an adjusting device, the adjusting device can axially displace relative to the first end cover, the acting force of the spring can be adjusted through the axial displacement of the adjusting device relative to the first end cover, and the inner control cavity is communicated with the inner oil return cavity.
A load sensitive flow distribution mechanism comprises the secondary flow distribution device, a rotary driving mechanism, a throttling port and a hydraulic pump, wherein an oil outlet in a valve body is connected with an inlet of the throttling port, a control oil port is communicated with an outlet of the throttling port, an outlet of the hydraulic pump is connected with an oil inlet, an oil return port is communicated with an inlet of the hydraulic pump, and the rotary driving mechanism can rotate to drive a shaft to rotate circumferentially.
The throttling opening is an adjustable throttling opening.
The invention has the following beneficial effects: the invention changes the axial position of the flow distribution shaft relative to the flow distribution sleeve, so that the diamond through hole is relative to the oil outlet triangular window, and the ratio of the oil outlet quantity to the oil return quantity can be adjusted. Because the position switching of the plurality of rhombic through holes and the plurality of oil outlet triangular windows and/or the plurality of oil return triangular serial ports realizes the on-off of the outer oil inlet cavity and the inner oil outlet cavity and/or the inner oil return cavity, when the rotation speed of the flow distribution shaft is high, the switching frequency of the valve port is high, the flow area of the valve port is large, and when the oil inlet is communicated with the oil outlet, the pressure of the oil inlet is similar to the pressure of the oil outlet; on the contrary, when the oil inlet is communicated with the oil return port, the pressure of the oil inlet is similar to the pressure of the oil return port. The flow of the oil outlet is the flow required by the system work, and the flow of the oil return port is the redundant flow which is not compressed and output by the hydraulic pump. Because the redundant oil that the oil return opening flows out does not pass through the hydraulic pump and compresses into high-pressure oil, so this partial flow's oil does not have extra waste energy.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is within the scope of the present invention for those skilled in the art to obtain other drawings based on the drawings without inventive exercise.
FIG. 1 is a schematic structural view of example 1 of the present invention;
FIG. 2 is a cross-sectional view taken along line A-A of FIG. 1;
FIG. 3 is an enlarged view of B in FIG. 2;
FIG. 4 is a schematic structural view of a port sleeve;
FIG. 5 is a schematic structural view of a port shaft;
FIG. 6 is a cross-sectional view of a port shaft;
FIG. 7 is a schematic view of the construction of the rotary drive shaft;
FIG. 8 is a schematic structural view of example 2 of the present invention;
FIG. 9 is a schematic structural view of example 3 of the present invention;
FIG. 10 is a schematic structural view of example 4 of the present invention
In the figure, 1, a valve body; 2, a valve shaft; 201, a first convex ring; 202, a second convex ring; 203, a third convex ring; 204, an oil outlet triangular window; 205, an oil return triangular window; 206, a chute; 207, a lubrication channel; 208, blind holes; 3, a flow distribution sleeve; 301, a first seal ring; 302, a second seal ring; 303, a third sealing ring; 304, a fourth seal ring; 305, a fifth seal ring; 306, a first via; 307, a second via; 308, diamond-shaped through holes; 309, a third via hole; 310, a fourth via hole; 4, a first end cover; 401, a spring limiting groove; 5, a second end cover; 501, an adapter; 502, a cover plate; 6, sealing a sleeve; 7, rotating the driving shaft; 8, a linkage pin; 9, ball bearings; 10, a spring seat; 11, a plane bearing; 12, a spring deformation quantity adjusting piece; 13, a choke; 14, a hydraulic pump; 15, a spring; 16, a rotation drive mechanism;
c1, an outer control oil chamber; a1, an oil outlet cavity; p1, outer oil inlet cavity; t1, outer oil return chamber; b1, an external controlled oil chamber;
c2, a control oil port; a2, oil outlet; p2, oil inlet; t2, oil return;
c3, an inner control oil chamber; a3, an oil outlet cavity is formed inside; t3, internal return chamber; b3, an internal controlled oil chamber.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention will be described in further detail with reference to the accompanying drawings.
It should be noted that all expressions using "first" and "second" in the embodiments of the present invention are used for distinguishing two entities with the same name but different names or different parameters, and it should be noted that "first" and "second" are merely for convenience of description and should not be construed as limitations of the embodiments of the present invention, and they are not described in any more detail in the following embodiments.
The terms of direction and position of the present invention, such as "up", "down", "front", "back", "left", "right", "inside", "outside", "top", "bottom", "side", etc., refer to the direction and position of the attached drawings. Accordingly, the use of directional and positional terms is intended to illustrate and understand the present invention and is not intended to limit the scope of the present invention.
Example 1:
as shown in fig. 1-7, a secondary flow distribution device comprises a valve body 1, wherein a cavity is arranged inside the valve body 1, two ends of the cavity are respectively connected with a first end cover 4 and a second end cover 5, a flow distribution shaft 2 and a flow distribution sleeve 3 sleeved outside the flow distribution shaft 2 are arranged in the valve body 1, two ends of the flow distribution sleeve 3 are respectively abutted against the first end cover 4 and the second end cover 5, and the flow distribution sleeve 3 is in linkage fit with the valve body 1;
the outer wall of the flow distribution sleeve 3 is sequentially provided with a first sealing ring 301, a second sealing ring 302, a third sealing ring 303, a fourth sealing ring 304 and a fifth sealing ring 305 along the axial direction, the outer walls of the first sealing ring 301, the second sealing ring 302, the third sealing ring 303, the fourth sealing ring 304 and the fifth sealing ring 305 are in sealing fit with the inner wall of the valve body 1, so that an outer control oil cavity C1, an outer oil outlet cavity A1, an outer oil inlet cavity P1, an outer oil return cavity T1 and an outer controlled oil cavity B1 which are separated and sequentially arranged along the axial direction are formed between the flow distribution sleeve 3 and the valve body 1, and the valve body 1 is provided with a control oil port C2 communicated with the outer control oil cavity C1, an oil outlet A2 communicated with the outer oil outlet cavity A1, an oil inlet P2 communicated with the outer oil inlet cavity P1, an oil return port T2 communicated with the outer oil return cavity T1 and a channel communicated with the outer controlled oil cavity A1 and the outer controlled oil cavity B1;
the outer wall of the flow distribution shaft 2 is sequentially provided with a first convex ring 201, a second convex ring 202 and a third convex ring 203 along the axial direction, the outer walls of the first convex ring 201, the second convex ring 202 and the third convex ring 203 are matched with the inner wall of the flow distribution sleeve 3, so that an inner oil outlet cavity A3 formed between the first convex ring 201 and the second convex ring 202 and an inner oil return cavity T3 formed between the second convex ring 202 and the third convex ring 203 are formed between the flow distribution shaft 2 and the flow distribution sleeve 3, an inner control oil cavity C3 formed between the side surface of the first convex ring 201 close to the first end cover 4 and the flow distribution sleeve 3, the end surface of the flow distribution shaft 2 and the first end cover 4, a sealing sleeve 6 is arranged at the side of the third convex ring 203 close to the second end cover 5, an inner controlled oil cavity B3 is formed between the sealing sleeve 6, the third convex ring 203, the inner wall of the flow distribution sleeve 3 and the outer wall of the flow distribution shaft 2, and a through hole 36306 for communicating the outer control oil cavity C1 and the inner control oil cavity 3 are arranged on the flow distribution sleeve 3, A second through hole 307 communicating the outer oil outlet chamber A1 with the inner oil outlet chamber A3, a third through hole 309 communicating the outer oil return chamber T1 with the inner oil return chamber T3, and a fourth through hole 310 communicating the outer controlled oil chamber B1 with the inner controlled oil chamber B3;
a plurality of rhombic through holes 308 which are uniformly distributed along the circumferential direction are formed between the second sealing ring 302 and the third sealing ring 303 on the flow distribution sleeve 3, a plurality of oil outlet triangular windows 204 which are uniformly distributed along the circumferential direction and are close to the inner oil outlet cavity A3 and a plurality of oil return triangular windows 205 which are close to the inner oil return cavity T3 are respectively formed at two ends of the second convex ring 202, and the oil outlet triangular windows 204 and the oil return triangular windows 205 are arranged in a staggered mode; the number of the oil outlet triangular windows 204, the number of the oil return triangular windows 205 and the number of the diamond-shaped through holes 308 are consistent;
a rotary driving shaft 7 penetrates through the second end cover 5, the rotary driving shaft 7 is in circumferential linkage fit with the port shaft 2, and the port shaft 2 can axially slide relative to the rotary driving shaft 7;
the valve shaft 2 and the first end cover 4 are provided with springs 15, and the springs 15 form pushing force or pulling force on the valve shaft 2;
the flow distribution shaft 2 is provided with a first position at which the rhombic through hole 308 is communicated with/disconnected from the inner oil outlet cavity A3 through switching the positions of the rhombic through hole 204 in the circumferential rotation state of the flow distribution shaft 2, a second position at which the rhombic through hole 308 is alternately communicated with the inner oil outlet cavity A3 and the inner oil return cavity T3 through switching the alternate positions of the oil outlet triangular window 204 and the oil return triangular window 205 in the circumferential rotation state of the flow distribution shaft 2, and a third position at which the rhombic through hole 308 is communicated with/disconnected from the inner oil return cavity T3 through switching the positions of the oil return triangular window 205 in the circumferential rotation state of the flow distribution shaft 2.
The tips of the diamond-shaped through hole 308, the oil outlet triangular window 204 and the oil return triangular window 205 are in rounded transition.
The outer end of the rotary drive shaft 7 may be connected to the motor shaft by a coupling or directly.
As shown in fig. 7, a linkage pin 8 is arranged at an end of the rotary drive shaft 7, a ball bearing 9 is fixed at each of two ends of the linkage pin 8, a sliding groove 206 adapted to the linkage pin 8 and the ball bearings 9 at two ends is arranged at one end of the port shaft 2 close to the second end cap 5, and the linkage pin 8 and the ball bearings 9 at two ends are located in the sliding groove 206 so that the rotary drive shaft 7 and the port shaft 2 are in circumferential linkage and can slide axially. The ball bearing 9 is in clearance fit with the port shaft 2, is in unilateral contact when stressed and can rotate forwards or reversely, and the rotary driving shaft 7 drives the port shaft 2 to rotate circumferentially and does not interfere with the axial displacement of the port shaft 2 under the action of hydraulic pressure and a spring.
The port shaft 2 is provided with a lubricating channel 207 communicating the chute 206 and the inner oil outlet cavity A3. The hydraulic oil in the inner oil outlet chamber a3 enters the slide groove 206 through the lubrication channel 207, and forms a lubrication effect on the ball bearing 9. As shown in fig. 2, a bearing is also provided between the rotary drive shaft 7 and the second end cap 5, and the hydraulic oil in the internal oil outlet chamber a3 also lubricates the bearing between the rotary drive shaft 7 and the second end cap 5, and the hydraulic pressure between the rotary drive shaft 7 and the second end cap 5 is close to 0.
As shown in fig. 2 and 3, the sealing sleeve 6 is annular, two end faces of the sealing sleeve 6 are planes, one end face of the sealing sleeve abuts against the second end cover 5, the inner wall of the sealing sleeve 6 is in clearance seal fit with the outer wall of the port shaft 2, and the outer wall of the sealing sleeve 6 is in clearance seal fit with the inner wall of the port sleeve 3.
The second end cap 5 comprises an adapter 501 and a cover plate 502 which are separated, and the cover plate 502, the adapter 501 and the valve body 1 are sequentially connected through bolts; the adapter 501 is sleeved outside the port shaft 2 and is in clearance fit with the port shaft 2; two ends of the flow distribution sleeve 3 are respectively abutted against the first end cover 4 and the adaptor 501; the end surface of the sealing sleeve 6 is abutted against the adapter 501. This is more stable.
The flow distribution shaft 2 is provided with a blind hole 208 near the first end cover 4, the blind hole 208 is limited by a spring seat 10, the inner end face of the first end cover 4 is provided with a spring limiting groove 401, and two ends of the spring 15 are limited by the spring seat 10 and the spring limiting groove 401 respectively.
The specific working process of this embodiment is as follows:
setting the pressure of the inner control oil chamber C3 (namely the control oil port C2) to be P1, and setting the action area of the inner control oil chamber C3 to be S1 (namely the total area of the end surfaces of the flow distribution shaft 2); the set pressure of the internal controlled oil chamber B3 (namely, the oil outlet A2) is P2, the acting area of the internal controlled oil chamber B3 is S2 (namely, the side wall area of the third convex ring 203), and S1 is more than S2, so the control oil is hydraulic oil which is smaller than the pressure of the outlet oil liquid.
The force analysis of the port shaft 2 in the equilibrium state is as follows:
P1S1+FK＝P2S2，Fkthe thrust or the tension of the spring (the thrust is positive and the tension is negative) when the port shaft 2 is in a balanced state.
FkIn particular, in order to reduce the influence of the change of the compression amount of the spring on the force balance state of the distributing shaft, the spring stiffness should be as small as possible, so that the hydraulic force is far larger than the spring force.
From the above, by reasonably setting the magnitude relationship of S1, S2 and the spring constant K, the proportional relationship between the set pressure P2 at the oil outlet a2 and the pressure P1 at the control port C2 can be established, and the set pressure P2 at the oil outlet a2 can be changed by adjusting the pressure P1 at the control port C2.
As shown in fig. 2, the pressure value P1 of the control oil port is unchanged, when the flow rate demanded by the system increases, the pressure at the oil outlet a2 decreases, the balance state at the two ends of the port shaft 2 is broken and starts to move upwards, the valve port occupation ratio formed by the oil outlet triangular window 204 and the rhombic through hole 308 increases, the opening time is prolonged, and more fluid flows to the oil outlet; conversely, when the required flow of the system is reduced, the pressure at the oil outlet a2 is increased, the balance state at the two ends of the port shaft 2 is broken and moves downwards, the opening degree of the valve port formed by the oil outlet triangular window 204 and the rhombic through hole 308 is reduced, the opening time is reduced, the opening degree of the valve port formed by the oil return triangular window 205 and the rhombic through hole 308 is increased, the opening time is increased, more flow flows back to the oil tank, the flow of the oil outlet is reduced, and the original force balance is achieved.
When the pressure value P1 of the control oil port is increased, the balance state at the two ends of the port shaft 2 is broken, the port shaft starts to move upwards, the opening degree of a valve port formed by the oil outlet triangular window 204 and the rhombic through hole 308 is increased, the opening time is prolonged, more fluid flows to the oil outlet, the pressure of the inner control oil cavity C3 is increased until the forces at the two ends of the port shaft 2 are balanced again; and vice versa.
Example 2:
different from the embodiment 1, a spring limiting groove 401 is formed in the inner end surface of the first end cover 4, the spring 15 is limited in the spring limiting groove 401, a plane bearing 11 is arranged between the spring 15 and the end surface of the flow distribution shaft 2, and a gap is formed between the outer wall of the plane bearing 11 and the inner wall of the spring limiting groove 401; the spring 15 remains contracted. Compared with embodiment 1, the present embodiment has no influence on the spring 15 when the port shaft 2 rotates at a high speed by providing the flat bearing 11.
Example 3:
as shown in fig. 9, unlike embodiment 1, in this embodiment, a control oil port C2 communicating with an inner control chamber C3 is not provided on the valve body 1, but an adjusting device 12 is connected to the first end cap 4, the adjusting device 12 is axially displaceable relative to the first end cap 4, the acting force of the spring 15 is adjusted by the axial displacement of the adjusting device 12 relative to the first end cap 4, and the inner control chamber C3 communicates with an inner oil return chamber T3 to make the hydraulic action in the inner control chamber C3 approach to 0.
The specific settings are as follows: adjusting device 12 and first end cover 4 threaded connection, the both ends of spring 15 are equipped with a spring holder 10 respectively, a spring holder butt flow distribution shaft 2, another spring holder butt adjusting device 12, when rotatory adjusting device 12, the distance between two spring holders 10 changes, thereby make the effort increase or reduce of spring, flow distribution shaft 2, be equipped with the passageway of intercommunication interior oil return chamber T3 and interior control chamber C3 on the spring holder 10, make interior control chamber C3 and interior oil return chamber T3 communicate and make the hydraulic action in the interior control chamber C3 be close to 0. The acting forces at the two ends of the port shaft 2 are respectively the thrust of the spring 15 and the hydraulic pressure of the inner controlled oil chamber B3, and the balance of the port shaft 2 is broken by adjusting the acting force of the spring 15 or the pressure change of the inner controlled oil chamber B3, so that the port shaft 2 moves. The adjustment device 12 is a manually rotatable adjustment member. A plane bearing is arranged between the spring 15 and the spring seat 10 of the spring 15, so that the stability, accuracy and durability of the spring 15 can be improved.
Example 4:
as shown in fig. 10, a load-sensitive flow distribution mechanism includes a secondary flow distribution device as described in embodiment 1, embodiment 2, or embodiment 3, a rotary drive mechanism 16, a choke 13, and a hydraulic pump 14, an oil outlet a2 on the valve body 1 is connected to an inlet of the choke 13, a control oil port C2 is communicated with an outlet of the choke 13, an outlet of the hydraulic pump 14 is connected to an oil inlet P2, an oil return port T2 is communicated with an inlet of the hydraulic pump 14, and the rotary drive mechanism can rotate the drive shaft 7 to rotate circumferentially.
The throttling opening 13 is an adjustable throttling opening.
Common hydraulic control systems are open-center and closed-center hydraulic systems. The middle open type hydraulic system is used for limiting the highest working pressure of the system, and a high-pressure overflow valve is required to be arranged. When the system operating pressure reaches the set point, nearly all of the hydraulic pump flow will flow back through the relief valve to the tank, resulting in very high power losses and significant heat losses in the system resulting in very low system efficiency. The hydraulic pump of the hydraulic system with closed center realizes displacement adjustment near the defined highest working pressure under all working conditions. However, in the case of low-pressure, high-flow operating conditions, a relatively high pressure drop occurs and a large amount of heat is generated in the course of energy loss.
An ideal system would have such a characteristic: providing only the necessary flow to maintain system operation at the operating pressure required by the load. Both the desired flow rate and the operating pressure are variable, but neither open nor closed systems provide such performance. To achieve this characteristic, a new hydraulic pump must be designed, which can provide the necessary flow and pressure according to the system requirements and has a corresponding pressure-flow regulation function when the working condition changes, and the hydraulic pump having this function is called a load-sensitive pump.
The flow output by the load-sensitive flow distribution mechanism is L, the pressure difference at two ends of the throttling port 13 is delta P, the area of the throttling port 13 is S,
as can be seen from the above equation, the output flow L is independent of the load pressure.
When the area of the throttle orifice 13 is constant, the output flow rate is related to the pressure difference between two ends of the throttle orifice 13, namely the difference between P1 and P2, and according to the force balance equation of the port shaft 2, the following are provided: P1S1+ Fk P2S2,
for example 1 and example 2, the force of Fk can be neglected,
it can be seen that the pressure differential is determined only by the pressure P1 in the inner control gallery C3 (i.e. control port C2),
it can be seen that L is a value associated with only P1, and when P1 is unchanged, the output flow L is constant; by adjusting P1, the output flow L can be adjusted;
for example 3, the optimized structure is that S1 is S2,
it can be seen that the pressure difference is set solely by the spring force,
therefore, when the spring force is unchanged, the output flow L is a constant value; by adjusting the force of the spring, the flow L of the output can be adjusted.
It will be understood by those skilled in the art that all or part of the steps in the method for implementing the above embodiments may be implemented by relevant hardware instructed by a program, and the program may be stored in a computer-readable storage medium, such as ROM/RAM, magnetic disk, optical disk, etc.
The above disclosure is only for the purpose of illustrating the preferred embodiments of the present invention, and it is therefore to be understood that the invention is not limited by the scope of the appended claims.
Claims (10)
1. A secondary flow distribution device is characterized in that: the valve comprises a valve body (1), wherein a cavity is formed in the valve body (1), two ends of the cavity are respectively connected with a first end cover (4) and a second end cover (5), a flow distribution shaft (2) and a flow distribution sleeve (3) sleeved outside the flow distribution shaft (2) are arranged in the valve body (1), two ends of the flow distribution sleeve (3) are respectively abutted against the first end cover (4) and the second end cover (5), and the flow distribution sleeve (3) is in linkage fit with the valve body (1);
the outer wall of the flow distribution sleeve (3) is sequentially provided with a first sealing ring (301), a second sealing ring (302), a third sealing ring (303), a fourth sealing ring (304) and a fifth sealing ring (305) along the axial direction, the outer walls of the first sealing ring (301), the second sealing ring (302), the third sealing ring (303), the fourth sealing ring (304) and the fifth sealing ring (305) are in sealing fit with the inner wall of the valve body (1) to form an outgoing oil cavity (A1), an external oil inlet cavity (P1), an external oil return cavity (T1) and an external controlled oil cavity (B1) which are separated from each other and sequentially arranged along the axial direction between the flow distribution sleeve (3) and the valve body (1), an oil outlet (A2) communicated with an outgoing oil cavity (A1), an oil inlet (P2) communicated with an external oil inlet cavity (P1), an oil return port (T2) communicated with an external oil return cavity (T1) and a channel communicated with an outgoing oil cavity (A1) and an external controlled oil cavity (B1) are arranged on the valve body (1);
the outer wall of the flow distribution shaft (2) is sequentially provided with a first convex ring (201), a second convex ring (202) and a third convex ring (203) along the axial direction, the outer walls of the first convex ring (201), the second convex ring (202) and the third convex ring (203) are matched with the inner wall of the flow distribution sleeve (3) to enable an inner oil outlet cavity (A3) formed between the first convex ring (201) and the second convex ring (202) and an inner oil return cavity (T3) formed between the second convex ring (202) and the third convex ring (203) to be formed between the flow distribution shaft (2) and the flow distribution sleeve (3), the end face of the flow distribution shaft (2) and the first end cover (4) to be formed with an inner control cavity (C3), one side of the third convex ring (203) close to the second end cover (5) is provided with a sealing sleeve (6), and the sealing sleeve (6) and the third convex ring (203) are arranged on one side of the sealing sleeve (5), An inner controlled oil cavity (B3) is formed between the inner wall of the flow distribution sleeve (3) and the outer wall of the flow distribution shaft (2), a second through hole (307) for communicating the outer oil outlet cavity (A1) with the inner oil outlet cavity (A3), a third through hole (309) for communicating the outer oil return cavity (T1) with the inner oil return cavity (T3), and a fourth through hole (310) for communicating the outer controlled oil cavity (B1) with the inner controlled oil cavity (B3);
a plurality of rhombic through holes (308) which are uniformly distributed along the circumferential direction are formed in the flow distribution sleeve (3) between the second sealing ring (302) and the third sealing ring (303), a plurality of oil outlet triangular windows (204) which are uniformly distributed along the circumferential direction and are close to the inner oil outlet cavity (A3) and a plurality of oil return triangular windows (205) which are uniformly distributed along the circumferential direction and are close to the inner oil return cavity (T3) are respectively formed in the two ends of the second convex ring (202), and the plurality of oil outlet triangular windows (204) and the plurality of oil return triangular windows (205) are arranged in a staggered mode; the number of the oil outlet triangular windows (204), the number of the oil return triangular windows (205) and the number of the rhombic through holes (308) are consistent;
a rotary driving shaft (7) penetrates through the second end cover (5), the rotary driving shaft (7) is in circumferential linkage fit with the flow distribution shaft (2), and the flow distribution shaft (2) can axially slide relative to the rotary driving shaft (7);
the flow distribution shaft (2) and the first end cover (4) are provided with springs (15), and the springs (15) form thrust on the flow distribution shaft (2);
the valve body (1) is provided with a control oil port (C2) communicated with the inner control cavity (C3) and/or a regulating device (12) for controlling the compression amount of the spring (15);
the flow distribution shaft (2) axially slides relative to the rotary driving shaft (7) and is provided with a diamond-shaped through hole (308), a first position communicated/disconnected with an inner oil outlet cavity (A3) is realized through position switching with an oil outlet triangular window (204) in the circumferential rotation state of the flow distribution shaft (2), a second position alternately communicated with the inner oil outlet cavity (A3) and an inner oil return cavity (T3) is realized through alternating position switching with the oil outlet triangular window (204) and an oil return triangular window (205) in the circumferential rotation state of the flow distribution shaft (2) by the diamond-shaped through hole (308), and a third position communicated/disconnected with the inner oil return cavity (T3) is realized through position switching with the oil return triangular window (205) in the circumferential rotation state of the flow distribution shaft (2).
2. The secondary flow distribution device of claim 1, wherein: the end part of the rotary driving shaft (7) is provided with a linkage pin (8), two ends of the linkage pin (8) are respectively fixed with a ball bearing (9), one end of the valve shaft (2) close to the second end cover (5) is provided with a chute (206) matched with the linkage pin (8) and the ball bearings (9) at two ends, and the linkage pin (8) and the ball bearings (9) at two ends are located in the chute (206) to enable the rotary driving shaft (7) to be circumferentially linked with the valve shaft (2) and to axially slide.
3. The secondary flow distribution device of claim 2, wherein: and a lubricating channel (207) which is communicated with the sliding groove (206) and the inner oil outlet cavity (A3) is arranged on the valve shaft (2).
4. The secondary flow distribution device of claim 1, wherein: the sealing sleeve (6) is in a ring shape, two end faces of the sealing sleeve (6) are planes, one end face of the sealing sleeve is abutted to the second end cover (5), the inner wall of the sealing sleeve (6) is in clearance seal fit with the outer wall of the flow distribution shaft (2), and the outer wall of the sealing sleeve (6) is in clearance seal fit with the inner wall of the flow distribution sleeve (3).
5. The secondary flow distribution device of claim 4, wherein: the second end cover (5) comprises an adapter piece (501) and a cover plate (502) which are separated, and the cover plate (502), the adapter piece (501) and the valve body (1) are sequentially connected through bolts; the adapter (501) is sleeved outside the valve shaft (2) and is in clearance fit with the valve shaft (2); two ends of the flow distribution sleeve (3) are respectively abutted against the first end cover (4) and the adaptor (501); the end face of the sealing sleeve (6) is abutted to the adapter piece (501).
6. The secondary flow distribution device of claim 1, wherein: be equipped with outer control chamber (C1) between valve body (1) and flow distribution sleeve (3), be equipped with first through-hole (306) that communicate outer control chamber (C1) and interior control chamber (C3) on flow distribution sleeve (3), be equipped with control hydraulic fluid port (C2) of communicating outer control chamber (C1) on valve body (1), flow distribution shaft (2) are close first end cover (4) and are equipped with a blind hole (208), blind hole (208) are spacing to have spring holder (10), the terminal surface is equipped with a spring spacing groove (401) in first end cover (4), the both ends of spring (15) are spacing through spring holder (10) and spring spacing groove (401) respectively.
7. The secondary flow distribution device of claim 1, wherein: an outer control cavity (C1) is arranged between the valve body (1) and the flow distribution sleeve (3), a first through hole (306) communicated with the outer control cavity (C1) and the inner control cavity (C3) is formed in the flow distribution sleeve (3), a control oil port (C2) communicated with the outer control cavity (C1) is formed in the valve body (1), a spring limiting groove (401) is formed in the inner end face of the first end cover (4), the spring (15) is limited in the spring limiting groove (401), a plane bearing (11) is arranged between the spring (15) and the end face of the flow distribution shaft (2), and a gap is formed between the outer wall of the plane bearing (11) and the inner wall of the spring limiting groove (401); the spring (15) remains in a contracted state.
8. The secondary flow distribution device of claim 1, wherein: the first end cover (4) is connected with an adjusting device (12), the adjusting device (12) can axially displace relative to the first end cover (4), the acting force of the spring (15) can be adjusted through the axial displacement of the adjusting device (12) relative to the first end cover (4), and an inner control cavity (C3) is communicated with an inner oil return cavity (T3).
9. A load-sensitive distribution mechanism, characterized by: the secondary flow distribution device comprises the secondary flow distribution device as claimed in any one of claims 1 to 8, a rotary driving mechanism (16), a throttling port (13) and a hydraulic pump (14), wherein an oil outlet (A2) on the valve body (1) is connected with an inlet of the throttling port (13), a control oil port (C2) is communicated with an outlet of the throttling port (13), an outlet of the hydraulic pump (14) is connected with an oil inlet (P2), an oil return port (T2) is communicated with an inlet of the hydraulic pump (14), and the rotary driving mechanism can drive the rotary driving shaft (7) to rotate circumferentially.
10. The load-sensitive flow distribution mechanism of claim 9, wherein: the throttling opening (13) is an adjustable flow opening.
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Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2211475C2 (en) * | 2001-08-14 | 2003-08-27 | Закрытое акционерное общество Производственное объединение "Джет" | Pressure regulator |
| CN202597311U (en) * | 2012-05-14 | 2012-12-12 | 宁波海宏液压有限公司 | Load sensing valve |
| CN204344558U (en) * | 2014-10-09 | 2015-05-20 | 镇江四联机电科技有限公司 | A kind of secondary electro-hydraulic servo control valve unit by finite angle motor direct-drive |
| CN204553385U (en) * | 2015-02-11 | 2015-08-12 | 徐工集团工程机械股份有限公司 | Valve core of multiway valve, load sensing multi-way valve and excavator |
| CN108412831A (en) * | 2018-05-09 | 2018-08-17 | 河北华春液压汽配有限公司 | Shunt variable voltage control commutation pile-up valve |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7921880B2 (en) * | 2007-08-20 | 2011-04-12 | Hydraforce, Inc. | Three-way poppet valve with intermediate pilot port |
-
2020
- 2020-08-18 CN CN202010831551.8A patent/CN112049828B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| RU2211475C2 (en) * | 2001-08-14 | 2003-08-27 | Закрытое акционерное общество Производственное объединение "Джет" | Pressure regulator |
| CN202597311U (en) * | 2012-05-14 | 2012-12-12 | 宁波海宏液压有限公司 | Load sensing valve |
| CN204344558U (en) * | 2014-10-09 | 2015-05-20 | 镇江四联机电科技有限公司 | A kind of secondary electro-hydraulic servo control valve unit by finite angle motor direct-drive |
| CN204553385U (en) * | 2015-02-11 | 2015-08-12 | 徐工集团工程机械股份有限公司 | Valve core of multiway valve, load sensing multi-way valve and excavator |
| CN108412831A (en) * | 2018-05-09 | 2018-08-17 | 河北华春液压汽配有限公司 | Shunt variable voltage control commutation pile-up valve |
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Application publication date: 20201208 Assignee: TEJI VALVE GROUP Co.,Ltd. Assignor: Wenzhou University Contract record no.: X2023330000105 Denomination of invention: A secondary flow distribution device and load sensitive flow distribution mechanism Granted publication date: 20220422 License type: Common License Record date: 20230311 |