CN111255763A - Hydraulic reversing valve - Google Patents
Hydraulic reversing valve Download PDFInfo
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- CN111255763A CN111255763A CN202010079481.5A CN202010079481A CN111255763A CN 111255763 A CN111255763 A CN 111255763A CN 202010079481 A CN202010079481 A CN 202010079481A CN 111255763 A CN111255763 A CN 111255763A
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- 230000000149 penetrating effect Effects 0.000 claims description 3
- 238000004519 manufacturing process Methods 0.000 abstract description 4
- 230000010354 integration Effects 0.000 abstract 1
- 238000013016 damping Methods 0.000 description 9
- 238000004891 communication Methods 0.000 description 7
- 238000000034 method Methods 0.000 description 7
- 230000000694 effects Effects 0.000 description 4
- 125000004122 cyclic group Chemical group 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 239000004484 Briquette Substances 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000002131 composite material Substances 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
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- Multiple-Way Valves (AREA)
Abstract
The invention belongs to the technical field of hydraulic valves. The invention discloses a hydraulic reversing valve which comprises a shell, a valve core, a left plunger, a left spring, a right plunger and a right spring, wherein the shell is provided with a port P, a port T, a port A and a port B, the valve core is positioned in the shell, the left plunger and the left spring are positioned at the left end of the shell, the right plunger and the right spring are positioned at the right end of the shell, a left oil return cavity, a left control cavity, a right oil return cavity and a right control cavity are formed in the shell, and the port A and the port B can be controlled by axial movement of the valve core to be alternately communicated with the port P, the left oil return cavity and the right oil return cavity, so that automatic reversing control is. The hydraulic reversing valve is simple and compact in structure, low in manufacturing cost and high in integration level.
Description
Technical Field
The invention belongs to the technical field of hydraulic valves, and particularly relates to a hydraulic reversing valve.
Background
Some hydraulically driven machines, such as balers, briquette machines, drum and can compacting machines, often require cyclic reciprocating motion, and hydraulic cylinders require cyclic reciprocating telescoping. In order to realize the automatic cyclic reciprocating action of the hydraulic cylinder, an electro-hydraulic control system is usually formed by a plurality of electromagnetic valve groups, corresponding pressure sensors, relays, controllers and the like in equipment. Although the hydraulic cylinder can be conveniently and automatically controlled in a reciprocating manner by the electro-hydraulic control system, the hydraulic system occupies a large space, is complex in pipeline connection, is difficult to quickly troubleshoot problems when a fault occurs, and has a large workload in the processes of maintenance, disassembly and assembly. In addition, when explosion-proof application is involved, the electromagnetic valve needs to adopt a special explosion-proof type electromagnetic valve, so that the production cost of equipment is greatly increased.
The invention patent with the application number of CN201811583353.3 and the name of 'composite automatic reversing valve' discloses a hydraulic valve capable of automatically reversing, which comprises a three-position five-way hydraulic control reversing valve, a first damping hole, a second damping hole, a third damping hole, a fourth damping hole, a first check valve, a second check valve, a third check valve, a fourth check valve, a fifth check valve, a sequence valve and a pilot overflow valve, wherein the three-position five-way hydraulic control reversing valve, the first damping hole, the second damping hole, the third damping hole, the fourth damping hole, the first check valve, the second check valve, the third check valve, the fourth check valve, the fifth check valve, the sequence valve and the pilot overflow valve are integrally installed on a valve block; the automatic reversing control of the three-position five-way hydraulic control reversing valve is realized by organically combining the damping hole, the one-way valve and the sequence valve to form a system pressure feedback and pilot control loop. Although the invention realizes the automatic control of the reversing valve only through the self pressure feedback loop without depending on an external electric control system, the oil circuit is particularly complex, the valve elements are more, the manufacturing and processing cost is high, the volume is large, and the invention is not suitable for popularization and application.
Disclosure of Invention
In order to solve the problems of the conventional hydraulic reversing valve, the invention provides a hydraulic reversing valve with a brand new structure. The hydraulic reversing valve comprises a valve shell, a valve core, a left plunger, a left spring, a right plunger and a right spring;
the shell is provided with a port P, a port T, a port A and a port B, the port P is connected with the oil inlet pipe, the port T is connected with the oil outlet pipe, and the port A and the port B are respectively connected with two oil cavities of the hydraulic cylinder;
the valve core is positioned in the shell and can axially reciprocate relative to the shell, a valve core through hole penetrating along the axial direction is formed in the valve core, the valve core through hole is of a structure with two large sides and a small middle part, a left oil return cavity is formed between the left end of the valve core and the shell, a right oil return cavity is formed between the right end of the valve core and the shell, and the left oil return cavity and the right oil return cavity are communicated with a T port;
the left plunger and the left spring are positioned at the left end of the shell, the left end of the left plunger can be matched in the shell in a left-right sliding mode, the right end of the left plunger is matched at the left end of the valve core through hole in a sliding mode, and when the left plunger moves rightwards, the valve core can be pushed to move rightwards; one end of the left spring is abutted against the shell, and the other end of the left spring is abutted against the left plunger, so that the left plunger keeps the trend of moving leftwards away from the valve core; a left control cavity is formed between the left end of the left plunger and the shell, and the left control cavity is communicated with the port B;
the right plunger and the right spring are positioned at the right end of the shell, the right end of the right plunger can be matched in the shell in a left-right sliding mode, the left end of the right plunger is matched at the right end of the valve core through hole in a sliding mode, and when the right plunger moves leftwards, the valve core can be pushed to move leftwards; one end of the second spring is abutted against the shell, and the other end of the second spring is abutted against the right plunger, so that the right plunger keeps the trend of moving rightwards to be far away from the valve core; a right control cavity is formed between the right end of the right plunger and the shell, and is communicated with the port A;
the axial movement of the valve core can control the port A and the port B to be alternately communicated with the port P, the left oil return cavity and the right oil return cavity; when the valve core is positioned at the right end position, the port A is communicated with the port P, the port B is communicated with the left oil return cavity, when the valve core is positioned at the left end position, the port B is communicated with the port P, and the port A is communicated with the right oil return cavity;
when the valve core is positioned at the right end position, and the pressure of the port A rises to the set pressure of a right spring, the pressure of a right control cavity pushes a right plunger piston to move leftwards, so that the valve core is pushed to move leftwards relative to the shell, the port B is communicated with the port P, the port A is communicated with a right oil return cavity, and the valve core is kept at the left end position by oil return backpressure in the right oil return cavity; when the valve core is at the left end position, the pressure of the port B rises to the set pressure of the left spring, the pressure of the left control cavity pushes the left plunger piston to move rightwards, the valve core is further pushed to move rightwards relative to the shell, the port A is communicated with the port P, the port B is communicated with the left oil return cavity, and the valve core is kept at the right end position by oil return backpressure in the left oil return cavity.
Preferably, the housing is provided with a first oil path, a second oil path, a third oil path and a fourth oil path;
one end of the first oil way is communicated with the left oil return cavity, and the other end of the first oil way is communicated with the T port; one end of the second oil way is communicated with the right oil return cavity, and the other end of the second oil way is communicated with the T port; one end of the third oil way is communicated with the left control cavity, and the other end of the third oil way is communicated with the port B; one end of the fourth oil way is communicated with the right control cavity, and the other end of the fourth oil way is communicated with the port A.
Further preferably, the first oil passage is provided with a first orifice, and the second oil passage is provided with a second orifice.
Preferably, the valve core is provided with a first oil hole and a second oil hole, one end of the first oil hole is communicated with the left oil return cavity, the other end of the first oil hole is selectively communicated with the port B, one end of the second oil hole is communicated with the right oil return cavity, the other end of the second oil hole is selectively communicated with the port A, the middle of the valve core is provided with an annular communicating groove, and the communicating groove is used for controlling the port P to be communicated with the port A or the port B.
Preferably, the valve core is provided with a third oil hole for communicating the valve core through hole with the left oil return cavity.
Preferably, the shell is provided with a first connecting groove; the first connecting groove is located between the shell and the cylinder barrel, is an annular groove distributed along the axial direction, and is communicated with the port P.
Preferably, a second connecting groove is formed in the shell; the second connecting groove is located between the shell and the valve core and is an annular groove distributed along the axial direction, one end of the second connecting groove is communicated with the port B, and the other end of the second connecting groove is selectively communicated with the first oil hole.
Preferably, a third connecting groove is formed in the shell; the third connecting groove is located in an annular groove which is formed between the shell and the valve core and is distributed along the axial direction, one end of the third connecting groove is communicated with the port A, and the other end of the third connecting groove is selectively communicated with the second oil hole.
Preferably, the shell adopts a split structure, and two ends of the shell are respectively provided with a detachable end cover.
Compared with the automatic reversing valve with the existing structure, the hydraulic reversing valve has the following beneficial technical effects:
1. in the invention, the valve core is driven by the left plunger, the left spring, the right plunger and the right spring to axially move relative to the shell to complete reversing.
2. In the invention, the oil way and the oil hole which are mutually related are arranged on the shell and the valve core, so that the alternative communication of the port A and the port B with the port P, the left oil return cavity and the right oil return cavity is completed in the relative axial movement process of the valve core relative to the shell. Therefore, the requirements on the use and control of the electromagnetic reversing valve in the existing automatic reversing process can be completely omitted, the cost and the control complexity are reduced, and the valve core can be reliably kept at the reversed position through the back pressure of the left oil return cavity and the right oil return cavity.
Drawings
FIG. 1 is a schematic structural view of a hydraulic directional control valve according to the present embodiment, in which a spool is in a right end position;
FIG. 2 is a schematic view of the cross-sectional structure A-A of FIG. 1;
FIG. 3 is a schematic structural diagram of the hydraulic directional control valve of the present embodiment when the spool is in the left end position;
fig. 4 is a schematic diagram of the application principle of the hydraulic directional valve of the embodiment.
Detailed Description
The technical solution of the present invention will be further described in detail with reference to the accompanying drawings and embodiments.
Referring to fig. 1, the hydraulic directional valve of the present embodiment includes a housing 1, a valve body 2, a left plunger 31, a left spring 41, a right plunger 32, and a right spring 42.
The shell 1 is of a hollow structure, the shell 1 is provided with a P port, a T port, an A port and a B port, the P port is connected with the oil inlet pipe, the T port is connected with the oil outlet pipe, and the A port and the B port are respectively connected with two oil cavities of the hydraulic cylinder. The valve core 2 is located inside the shell 1 and can axially reciprocate relative to the shell 1, a valve core through hole penetrating along the axial direction is formed in the valve core 2, the valve core through hole is of a structure with two large sides and a small middle part, a left oil return cavity 12 is formed between the left end of the valve core 2 and the shell 1, a right oil return cavity 13 is formed between the right end of the valve core 2 and the shell 1, and the left oil return cavity 12 and the right oil return cavity 13 are communicated with a T port.
The left plunger 31 and the left spring 41 are positioned at the left end of the shell 1, the left end of the left plunger 31 can be matched in the shell 1 in a left-right sliding mode, the right end of the left plunger 31 is matched in the left end of the valve core through hole in a sliding mode, and when the left plunger 31 moves rightwards, the valve core 2 can be pushed to move rightwards. One end of the left spring 41 is abutted against the shell 1, and the other end of the left spring is abutted against the left plunger 31, so that the left plunger 31 keeps the trend of moving away from the valve core 2 leftwards; a left control cavity 11 is formed between the left end of the left plunger 31 and the shell 1, and the left control cavity 11 is communicated with the port B.
The right plunger 32 and the right spring 42 are positioned at the right end of the shell 1, the right end of the right plunger 32 can be matched in the shell 1 in a left-right sliding mode, the left end of the right plunger 32 is matched at the right end of the valve core through hole in a sliding mode, and when the right plunger 32 moves leftwards, the valve core 2 can be pushed to move leftwards; the right spring 42 abuts the housing 1 at one end and the right plunger 32 at the other end, keeping the right plunger 32 in a tendency to move to the right. A right control chamber 14 is formed between the right end of the right plunger 32 and the housing 1, and the right control chamber 14 is communicated with the port a.
The axial movement of the valve core 2 can control the port A and the port B to be alternately communicated with the port P, the left oil return cavity 12 and the right oil return cavity 13. When the valve core 2 is at the right end position, the port A is communicated with the port P, the port B is communicated with the left oil return cavity 12, when the valve core 2 is at the left end position, the port B is communicated with the port P, and the port A is communicated with the right oil return cavity 13.
When the valve core 2 is at the right end position, the pressure of the port a rises to the set pressure of the right spring 42, the pressure of the right control cavity 14 pushes the left plunger 31 to move leftwards, and further drives the valve core 2 to move leftwards relative to the housing 1, so that the port B is communicated with the port P and the port a is communicated with the right oil return cavity 13, and the oil return backpressure in the right oil return cavity 13 keeps the valve core 2 at the left end position. When the valve core 2 is at the left end position, and the pressure of the port B rises to the set pressure of the left spring 41, the pressure of the left control cavity 11 pushes the left plunger 31 to move rightwards, and further drives the valve core 2 to move rightwards relative to the housing 1, so that the port a is communicated with the port P and the port B is communicated with the left oil return cavity 12, and the oil return backpressure in the left oil return cavity 12 keeps the valve core 2 at the right end position.
Referring to fig. 1, in the present embodiment, a first oil path 104, a second oil path 105, a third oil path 106 and a fourth oil path 107 are provided on the housing 1, one end of the first oil path 104 is communicated with the left oil return chamber 12, the other end is communicated with the T port, one end of the second oil path 105 is communicated with the right oil return chamber 13, and the other end is communicated with the T port; one end of the third oil passage 106 communicates with the left control chamber 13 and the other end communicates with the port B, and one end of the fourth oil passage 107 communicates with the right control chamber 14 and the other end communicates with the port a.
As shown in fig. 1, the first oil passage 104 is provided with the first orifice 61, and the second oil passage 105 is provided with the second orifice 62. At this time, by virtue of the throttling effect of the first throttling hole 61 and the second throttling hole 62 on the passing oil, namely the throttling effect on the oil flowing between the first oil path 104 and the left oil return cavity 12 and the throttling effect on the oil flowing between the second oil path 105 and the right oil return cavity 13, the acting force of the return oil back pressure in the left oil return cavity 12 on the valve core 2 in the direction pointing to the right oil return cavity 13 can be kept, the valve core 2 is fixed at the right end position, the port A and the port P are ensured, and the port B is stably communicated with the left oil return cavity 12; the acting force of the return oil back pressure in the right return oil cavity 13 on the valve core 2 in the direction pointing to the left return oil cavity 12 can be kept, the valve core 2 is fixed at the left end position, the port B and the port P are ensured, and the port A is stably communicated with the right return oil cavity 13.
Preferably, as shown in fig. 1, in this embodiment, the valve core 2 is provided with a first oil hole 21 and a second oil hole 22, one end of the first oil hole 21 is communicated with the left oil return chamber 12, the other end is selectively communicated with the port B, one end of the second oil hole 22 is communicated with the right oil return chamber 13, the other end is selectively communicated with the port a, an annular communicating groove 23 is provided in the middle of the valve core 2, and the communicating groove 23 is used for controlling the port P to be communicated with the port a or the port B. Thus, when the valve core 2 is at the left end position, the port P is communicated with the port B through the communication groove 23, and the port A is communicated with the right oil return cavity 13 through the second oil hole 22; when the valve core 2 is at the right end position, the port P is communicated with the port A through the communication groove 23, and the port B is communicated with the left oil return cavity 12 through the first oil hole 21.
Referring to fig. 2, in the present embodiment, a third oil hole 25 is formed in the valve core 2, and the third oil hole 25 connects the through hole of the valve core with the left chamber 12, so that the right end of the left plunger 31 and the left end of the right plunger 32 can be ensured to be connected with the T port, and when the left plunger 31 or the right plunger 32 moves, the pressure during reversing can be accurately controlled only by the force of the port B or the port a.
As shown in fig. 1, the housing 1 is further provided with a first connecting groove 101. The first connecting groove 101 is in the form of an annular groove structure arranged along the axial direction and is communicated with the port P.
As shown in fig. 1, a second connection groove 102 and a third connection groove 103 are also provided on the housing 1, respectively. The second connecting groove 102 and the third connecting groove 103 are both in the form of annular groove structures and are located between the housing 1 and the valve core 2, wherein one end of the second connecting groove 102 is in selective communication with the port B, the other end of the second connecting groove 102 is in selective communication with the first oil hole 21, one end of the third connecting groove 103 is in selective communication with the port a, and the other end of the third connecting groove 107 is in selective communication with the second oil hole 22.
In addition, as shown in fig. 1, in the present embodiment, the housing 1 is a split structure, and both ends of the housing are respectively in the form of end covers connected by axial bolts. Therefore, the whole shell is convenient to process and manufacture, particularly relevant oil ways, so that the processing difficulty and cost are reduced, the disassembly is convenient, and the assembly efficiency and the maintenance convenience are improved.
Referring to fig. 1 to 4, when the hydraulic directional control valve of the present embodiment works, the port P is connected to the outlet of the hydraulic pump 8, the port T is connected to the oil tank, and the port a and the port B are respectively connected to two oil chambers of the hydraulic cylinder 7, and the specific working process is as follows:
when the valve core 2 is positioned at the right end position, the port A is communicated with the port P, the port B is communicated with the left oil return cavity, the hydraulic cylinder 7 moves rightwards, high-pressure oil of the hydraulic pump 8 sequentially flows to the port A through the port P, the first connecting groove 101, the communicating groove 23 and the third connecting groove 103, and simultaneously the oil in the port B sequentially flows to the oil tank through the second connecting groove 102, the first oil hole 21, the left oil return cavity 12, the first oil way 104 and the port T, so that the hydraulic cylinder 7 moves rightwards under the action of pressure difference of the oil on two sides of the port A and the port B.
In the process, oil in the left oil return cavity 11 flows into the T port through the first throttle hole 61 in the first oil path 104, so that back pressure exists in the left oil return cavity 12, and at the moment, no oil flows in the right oil return cavity 13, and the pressure is equal to the pressure of the T port, so that the valve element 2 is fixed at the right end position under the action of the pressure difference between the oil on the two sides of the left oil return cavity 12 and the oil on the two sides of the right oil return cavity 13, the P port is communicated with the a port through the communicating groove 23, and the B port is communicated with the left oil return cavity 12 through the first oil hole 21, and the stability and reliability of the right movement.
When the hydraulic cylinder 7 moves to the uppermost position, the pressure in the port a rises rapidly, the pressure in the right control cavity 14 acts on the right plunger 32 to overcome the acting force of the right spring 42, the right plunger 32 is pushed to move leftwards, and the valve element 2 is further pushed to move leftwards, so that high-pressure oil at the outlet of the hydraulic pump 8 flows to the port B sequentially through the port P, the first connecting groove 101, the communicating groove 23 and the second connecting groove 102, meanwhile, the oil in the port a flows to an oil tank sequentially through the third connecting groove 103, the second oil hole 22, the right oil return cavity 13, the second oil path 105 and the port T, and due to the oil return back pressure in the right oil return cavity 13, the valve element 2 is fixed at the left end position under the action of the pressure difference of the oil at two sides of the right oil return cavity 13 and the left.
In the process, oil in the right oil return cavity 13 flows into the T port through the second throttle hole 62 in the second oil path 105, so that back pressure exists in the right oil return cavity 13, and at the moment, no oil flows in the left oil return cavity 12, and the pressure is equal to the pressure of the T port, so that the valve core 2 is fixed at the left end position under the action of the pressure difference between the oil at two sides of the right oil return cavity 13 and the oil at two sides of the left oil return cavity 12, the port P is kept to be communicated with the port B through the communicating groove 23, and the port a is communicated with the right oil return cavity 13 through the second oil hole 22, and the stability and reliability of the.
When the hydraulic cylinder 7 moves to the leftmost position, the pressure in the port B rises rapidly, the pressure in the left control chamber 11 acts on the left plunger 31 to overcome the acting force of the left spring 41, the left plunger 31 is pushed to move rightwards, further, the valve element 2 is pushed to move rightwards, so that the high-pressure oil of the hydraulic pump 8 flows to the port A through the port P, the first connecting groove 101, the communicating groove 23 and the third connecting groove 103 in sequence, meanwhile, the oil in the port B flows to the oil tank through the second connecting groove 102, the first oil hole 21, the left oil return cavity 12, the first oil path 104 and the port T in sequence, because the oil return back pressure exists in the left oil return cavity 12, the valve core 2 moves relative to the shell 1 in the direction of the right oil return cavity 13 under the action of the pressure difference of oil liquid on two sides of the left oil return cavity 12 and the right oil return cavity 13, the port P is switched to be communicated with the port A, the port B is switched to be communicated with the left oil return cavity 12, and the reversing operation of the hydraulic cylinder 7 is realized.
The reciprocating action is repeated in sequence, and the automatic reciprocating motion of the hydraulic cylinder is controlled by the hydraulic directional valve.
Claims (9)
1. A hydraulic reversing valve is characterized by comprising a shell, a valve core, a left plunger, a left spring, a right plunger and a right spring;
the shell is provided with a port P, a port T, a port A and a port B, the port P is connected with the oil inlet pipe, the port T is connected with the oil outlet pipe, and the port A and the port B are respectively connected with two oil cavities of the hydraulic cylinder;
the valve core is positioned in the shell and can axially reciprocate relative to the shell, a valve core through hole penetrating along the axial direction is formed in the valve core, the valve core through hole is of a structure with two large sides and a small middle part, a left oil return cavity is formed between the left end of the valve core and the shell, a right oil return cavity is formed between the right end of the valve core and the shell, and the left oil return cavity and the right oil return cavity are communicated with a T port;
the left plunger and the left spring are positioned at the left end of the shell, the left end of the left plunger can be matched in the shell in a left-right sliding mode, the right end of the left plunger is matched at the left end of the valve core through hole in a sliding mode, and when the left plunger moves rightwards, the valve core can be pushed to move rightwards; one end of the left spring is abutted against the shell, and the other end of the left spring is abutted against the left plunger, so that the left plunger keeps the trend of moving leftwards away from the valve core; a left control cavity is formed between the left end of the left plunger and the shell, and the left control cavity is communicated with the port B;
the right plunger and the right spring are positioned at the right end of the shell, the right end of the right plunger can be matched in the shell in a left-right sliding mode, the left end of the right plunger is matched at the right end of the valve core through hole in a sliding mode, and when the right plunger moves leftwards, the valve core can be pushed to move leftwards; one end of the second spring is abutted against the shell, and the other end of the second spring is abutted against the right plunger, so that the right plunger keeps the trend of moving rightwards to be far away from the valve core; a right control cavity is formed between the right end of the right plunger and the shell, and is communicated with the port A;
the axial movement of the valve core can control the port A and the port B to be alternately communicated with the port P, the left oil return cavity and the right oil return cavity; when the valve core is positioned at the right end position, the port A is communicated with the port P, the port B is communicated with the left oil return cavity, when the valve core is positioned at the left end position, the port B is communicated with the port P, and the port A is communicated with the right oil return cavity;
when the valve core is positioned at the right end position, and the pressure of the port A rises to the set pressure of a right spring, the pressure of a right control cavity pushes a right plunger piston to move leftwards, so that the valve core is pushed to move leftwards relative to the shell, the port B is communicated with the port P, the port A is communicated with a right oil return cavity, and the valve core is kept at the left end position by oil return backpressure in the right oil return cavity; when the valve core is at the left end position, the pressure of the port B rises to the set pressure of the left spring, the pressure of the left control cavity pushes the left plunger piston to move rightwards, the valve core is further pushed to move rightwards relative to the shell, the port A is communicated with the port P, the port B is communicated with the left oil return cavity, and the valve core is kept at the right end position by oil return backpressure in the left oil return cavity.
2. The hydraulic directional valve according to claim 1, wherein a first oil passage, a second oil passage, a third oil passage and a fourth oil passage are provided in the housing;
one end of the first oil way is communicated with the left oil return cavity, and the other end of the first oil way is communicated with the T port; one end of the second oil way is communicated with the right oil return cavity, and the other end of the second oil way is communicated with the T port; one end of the third oil way is communicated with the left control cavity, and the other end of the third oil way is communicated with the port B; one end of the fourth oil way is communicated with the right control cavity, and the other end of the fourth oil way is communicated with the port A.
3. The hydraulic directional control valve according to claim 2, wherein a first orifice is provided in the first oil passage, and a second orifice is provided in the second oil passage.
4. The hydraulic directional valve according to claim 2, wherein the valve core is provided with a first oil hole and a second oil hole, the first oil hole is communicated with the left oil return cavity at one end and selectively communicated with the port B at the other end, the second oil hole is communicated with the right oil return cavity at one end and selectively communicated with the port a at the other end, and an annular communicating groove is formed in the middle of the valve core and used for controlling the port P to be communicated with the port a or the port B.
5. The hydraulic directional valve according to claim 4, wherein the spool is provided with a third oil hole for communicating the spool through hole with the left oil return chamber.
6. The hydraulic directional valve as claimed in any one of claims 1 to 5, wherein the housing is provided with a first connecting groove; the first connecting groove is located between the shell and the valve core, is an annular groove distributed along the axial direction, and is communicated with the port P.
7. The hydraulic directional valve of claim 4, wherein the housing has a second attachment slot; the second connecting groove is located between the shell and the valve core and is an annular groove distributed along the axial direction, one end of the second connecting groove is communicated with the port B, and the other end of the second connecting groove is selectively communicated with the first oil hole.
8. The hydraulic directional valve of claim 4, wherein the housing has a third connecting slot; the third connecting groove is located in an annular groove which is formed between the shell and the valve core and is distributed along the axial direction, one end of the third connecting groove is communicated with the port A, and the other end of the third connecting groove is selectively communicated with the second oil hole.
9. The hydraulic directional valve according to any one of claims 1 to 8, wherein the housing is of a split structure, and both ends are respectively provided with a detachable end cover.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010079481.5A CN111255763B (en) | 2020-02-04 | 2020-02-04 | Hydraulic reversing valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010079481.5A CN111255763B (en) | 2020-02-04 | 2020-02-04 | Hydraulic reversing valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111255763A true CN111255763A (en) | 2020-06-09 |
| CN111255763B CN111255763B (en) | 2022-02-15 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010079481.5A Active CN111255763B (en) | 2020-02-04 | 2020-02-04 | Hydraulic reversing valve |
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| CN (1) | CN111255763B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114321439A (en) * | 2021-12-29 | 2022-04-12 | 湖北三江航天红峰控制有限公司 | Automatic reversing valve |
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| CN105864139A (en) * | 2016-05-18 | 2016-08-17 | 山东常林机械集团股份有限公司 | Hydraulic operated directional control valve |
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| US3073332A (en) * | 1959-05-28 | 1963-01-15 | Don S Strader | Pressure operated reciprocating hydraulic valve |
| US3906835A (en) * | 1974-01-14 | 1975-09-23 | Caterpillar Tractor Co | Fluid motor control system with manual and self-cycling modes of operation |
| DE4333788A1 (en) * | 1992-10-05 | 1994-04-07 | Dana Corp | Fluid control valve with adjustable operating point - includes springloaded slide with coupling to actuator piston and with adjustment stop to control load |
| US6082243A (en) * | 1997-03-15 | 2000-07-04 | Fev Motorentechnik Gmbh & Co. Kg | Fluid controlled switching unit |
| CN2413111Y (en) * | 1999-05-27 | 2001-01-03 | 孙涛 | Sequential valve capable of realizing several action sequence |
| US20050133098A1 (en) * | 2003-10-15 | 2005-06-23 | Tohru Ino | Normally open hydraulic control valve |
| CN101560998A (en) * | 2009-05-07 | 2009-10-21 | 刘常芝 | Self-control positioning bidirectional hydraulic change-over valve |
| CN102155154A (en) * | 2010-07-09 | 2011-08-17 | 兰州理工大学 | Pressure controlled automatic reversing working device for punch of rock drilling machine |
| CN201865999U (en) * | 2010-09-03 | 2011-06-15 | 巨隆集团芜湖兴隆液压有限公司 | Self-control two-position four-way reversing valve |
| CN105864139A (en) * | 2016-05-18 | 2016-08-17 | 山东常林机械集团股份有限公司 | Hydraulic operated directional control valve |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114321439A (en) * | 2021-12-29 | 2022-04-12 | 湖北三江航天红峰控制有限公司 | Automatic reversing valve |
| CN114321439B (en) * | 2021-12-29 | 2023-10-03 | 湖北三江航天红峰控制有限公司 | Automatic reversing valve |
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| CN111255763B (en) | 2022-02-15 |
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Address after: 325102 Sanqiao Industrial Zone, Oubei Town, Yongjia County, Wenzhou City, Zhejiang Province Patentee after: Zhejiang Mingguan Valve Co.,Ltd. Country or region after: China Address before: 325102 Sanqiao Industrial Zone, Oubei Town, Yongjia County, Wenzhou City, Zhejiang Province Patentee before: ZHEJIANG GUANLONG MACHINERY VALVE CO.,LTD. Country or region before: China |