CN212337750U - Rotary balance valve and rotary hydraulic system - Google Patents
Rotary balance valve and rotary hydraulic system Download PDFInfo
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- CN212337750U CN212337750U CN202021673950.8U CN202021673950U CN212337750U CN 212337750 U CN212337750 U CN 212337750U CN 202021673950 U CN202021673950 U CN 202021673950U CN 212337750 U CN212337750 U CN 212337750U
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Abstract
A rotary balance valve and a rotary hydraulic system are provided, wherein the rotary balance valve comprises: a shuttle valve having first and second shuttle valve inlets and a shuttle valve outlet; the first balance valve is provided with a first main working oil port and a first auxiliary working oil port; the second balance valve is provided with a second main working oil port and a second auxiliary working oil port; the overflow valve comprises a first overflow port, a second overflow port and an overflow valve external control port, and the overflow valve external control port is communicated with a pressure spring in the overflow valve; the oil duct comprises a first main oil duct, a second main oil duct and a pressurizing oil duct, the first main oil duct is communicated with a first shuttle valve inlet, a first auxiliary working oil port, a first main working oil port and a first overflow port, the second main oil duct is communicated with a second shuttle valve inlet, a second auxiliary working oil port, a second main working oil port and a second overflow port, and the pressurizing oil duct is communicated with a shuttle valve outlet and an overflow valve external control port. The utility model discloses be favorable to improving the stability of gyration balanced valve operation, improve the softness that rotation mechanism stopped.
Description
Technical Field
The utility model relates to a hydraulic control technical field especially relates to a gyration balanced valve and gyration hydraulic system.
Background
In the field of engineering machinery, the transmission mode of most working mechanisms is hydraulic transmission, that is, an engine drives a hydraulic pump to provide hydraulic energy, and a hydraulic control valve provides flow and maximum pressure for supporting actions for a hydraulic cylinder or a hydraulic motor, so that actions of mechanical equipment are realized.
When a slewing mechanism of equipment operates, a hydraulic motor provides power, the slewing inertia is large, the speed is often unstable during the operation, and when the slewing operation is stopped, the impact is very large, so that the equipment is damaged very greatly. Therefore, a rotary balance valve must be fitted in the rotary hydraulic motor circuit to stabilize its operation. At present, in order to reduce the impact of the equipment when the equipment stops rotating, an overflow valve is arranged at a motor oil port to be used as a buffer valve. However, when the swing mechanism operates, the overflow valve needs higher set pressure so as to prevent the overflow valve from being opened to cause the swing mechanism to be incapable of operating when the oil supply pressure is not enough to start the motor; when the slewing mechanism stops, the overflow valve needs lower set pressure so as to prevent the slewing mechanism from stopping and impacting too much, and at the moment, the overflow valve and the slewing mechanism are in conflict, so that the requirements of high-pressure starting and low-pressure braking are difficult to realize.
SUMMERY OF THE UTILITY MODEL
The technical problem solved by the utility model is to provide a gyration balance valve and gyration hydraulic system helps improving the stationarity that rotation mechanism moved, makes the start more steady, also is favorable to improving the softness when rotation mechanism stops, makes rotation mechanism steadily stop, avoids assaulting to improve gyration hydraulic system's stability and reliability.
In order to solve the above technical problem, an embodiment of the utility model provides a gyration balanced valve, include: a shuttle valve having a first shuttle valve inlet, a second shuttle valve inlet, and a shuttle valve outlet; a first balance valve having a first main working port and a first sub working port; a second balanced valve having a second main working port and a second sub working port; the overflow valve comprises a first overflow port, a second overflow port and an overflow valve external control port, a pressure spring is arranged in the overflow valve, and the overflow valve external control port is communicated with the pressure spring; the oil duct comprises a first main oil duct, a second main oil duct and a pressurizing oil duct, the first main oil duct is communicated with the first shuttle valve inlet, the first auxiliary working oil port, the first main working oil port and the first overflow port, the second main oil duct is communicated with the second shuttle valve inlet, the second auxiliary working oil port, the second main working oil port and the second overflow port, and the pressurizing oil duct is communicated with the shuttle valve outlet and the overflow valve external control port.
Optionally, when the overflow valve is single, the overflow valve is a two-way overflow valve, and the two-way overflow valve includes: the valve comprises a valve seat and a sleeve, wherein the valve seat is provided with a valve cavity, a first overflow port, a second overflow port and an overflow valve external control port; the valve core is arranged in the valve cavity and comprises a main body, a first bulge arranged at one end of the main body and a second bulge arranged at the other end of the main body, and the first bulge is used for plugging the first overflow port.
Optionally, the diameter of the main body is larger than the diameters of the first protrusion and the second protrusion, the main body is tightly attached to the inner wall of the valve chamber, a first gap is formed between the first protrusion and the inner wall of the valve chamber, and when the first protrusion blocks the first overflow port, the first gap is communicated with the second overflow port; and a second clearance is formed between the second bulge and the inner wall of the valve cavity, and the outer control port of the overflow valve is communicated with the second clearance.
Optionally, the top of the sleeve is connected with an adjusting rod, and the pressure spring is arranged between the adjusting rod and the second protrusion of the valve core.
Optionally, when a plurality of overflow valves are provided, the first overflow valve and the second overflow valve are included, and the first overflow valve and the second overflow valve are reversely connected in parallel between the first main oil gallery and the second main oil gallery.
Optionally, the first overflow valve includes a first overflow inlet, a first overflow outlet and a first overflow valve external control port, the second overflow valve includes a second overflow inlet, a second overflow outlet and a second overflow valve external control port, the first overflow inlet and the second overflow outlet are connected to the first overflow port, the first overflow outlet and the second overflow inlet are connected to the second overflow port, and the first overflow valve external control port and the second overflow valve external control port are connected to the overflow valve external control port.
Optionally, the first balance valve includes a first pressure valve and a first check valve, the first pressure valve has a first main working oil port and a first auxiliary working oil port, one end of the first check valve is connected to the first main working oil port, and the other end of the first check valve is connected to the first auxiliary working oil port; the second balance valve comprises a second pressure valve and a second check valve, the second pressure valve is provided with a second main working oil port and a second auxiliary working oil port, one end of the second check valve is connected with the second main working oil port, and the other end of the second check valve is connected with the second auxiliary working oil port.
Optionally, the first pressure valve has a first control oil port, the second pressure valve has a second control oil port, the first control oil port is connected to the second control oil port through a first branch oil duct, the first sub-working oil port is connected to the second sub-working oil port through a second branch oil duct, a connection oil duct is further disposed between the first branch oil duct and the second branch oil duct, a first end of the connection oil duct is located on the first branch oil duct, and a second end of the connection oil duct is located on the second branch oil duct; the rotary balance valve further comprises a first damping part and a second damping part, and the first damping part is positioned on the second branch oil passage between the second end of the connecting oil passage and the first auxiliary working oil port; the second damping piece is located between the second end of the connecting oil duct and the second auxiliary working oil port on the second branch oil duct.
Optionally, the damping coefficient of the second damping member is equal to the damping coefficient of the first damping member.
Optionally, the first pressure valve has a first control oil port, the second pressure valve has a second control oil port, the first sub-working oil port is connected with the second control oil port through a first branch oil passage, and the second sub-working oil port is connected with the first control oil port through a second branch oil passage.
The embodiment of the utility model provides a still provide a gyration hydraulic system, include as above arbitrary gyration balanced valve.
Optionally, the swing hydraulic system further includes: the hydraulic motor is provided with a first working port and a second working port, the first working port is connected with a first main working oil port and a first overflow port on the first main oil duct, and the second working port is connected with a second main working oil port and a second overflow port on the second main oil duct; the brake is used for braking the hydraulic motor and comprises an oil inlet, and the oil inlet of the brake is connected with the shuttle valve outlet of the shuttle valve.
Compared with the prior art, the utility model discloses technical scheme has following beneficial effect:
the outlet of the shuttle valve is connected with the outer control port of the overflow valve by arranging the pressurizing oil duct, the outer control port of the overflow valve is communicated with the pressure spring in the overflow valve, when the swing mechanism acts, a part of hydraulic oil flows into the overflow valve from the outer control port of the overflow valve, the pressure brought by the part of hydraulic oil and the elastic force of the set pressure spring act together to form the opening pressure required for opening the overflow valve, and the pressure increasing oil duct is arranged, so that the overflow valve cannot be opened when the swing mechanism acts, and the overflow valve is prevented from being opened to cause the abnormal operation of the swing mechanism; when the slewing mechanism stops, the oil is not fed into the pressurizing oil duct, and the opening pressure required for opening the overflow valve is the elastic force of the set pressure spring, so that the overflow valve is easy to open when the slewing mechanism stops, the impact when the slewing mechanism stops is reduced, and the high-pressure starting and low-pressure braking of the slewing balance valve are realized.
Drawings
FIG. 1 is a hydraulic schematic of a balancing valve block in one embodiment;
fig. 2 and 3 are hydraulic schematic diagrams of a rotary balanced valve according to an embodiment of the present invention;
FIG. 4 is a hydraulic schematic diagram of a rotary balanced valve according to another embodiment of the present invention;
fig. 5 is a hydraulic schematic diagram of a rotary hydraulic system according to an embodiment of the present invention;
fig. 6 is a schematic structural view of the relief valve shown in fig. 2.
Detailed Description
As known from the background art, the existing balance valve group is not stable enough when the slewing mechanism runs and stops, and is easy to impact hydraulic elements.
Now considering an analysis in connection with a balanced valve group 10, with reference to fig. 1, said balanced valve group 10 comprises:
a shuttle valve 20, the shuttle valve 20 having a first shuttle valve inlet 21, a second shuttle valve inlet 22, and a shuttle valve outlet 23;
a first balance valve 30, wherein the first balance valve 30 includes a first pressure valve 31 and a first check valve 32, the first pressure valve 31 has a first main working port a1 and a first sub working port b1, and the first check valve 32 is connected to the first main working port a1 and the first sub working port b 1;
a second balance valve 40, wherein the second balance valve 40 includes a second pressure valve 41 and a second check valve 42, the second pressure valve 41 has a second main working port a2 and a second auxiliary working port b2, and the second check valve 42 connects the second main working port a2 and the second auxiliary working port b 2;
a first spill valve 50, said first spill valve 50 having a first oil inlet 51 and a first oil outlet 52;
a second spill valve 60, said second spill valve 60 having a second oil inlet 61 and a second oil outlet 62;
and the oil passage comprises a first main oil passage 71 and a second main oil passage 72, the first main oil passage 71 is communicated with the first shuttle valve inlet 21, the first auxiliary working oil port b1, the first main working oil port a1, the first oil inlet 51 and the second oil outlet 62, and the second main oil passage 72 is communicated with the second shuttle valve inlet 22, the second auxiliary working oil port b2, the second main working oil port a2, the second oil inlet 52 and the first oil return port 61.
A first hydraulic oil inlet v1 is provided on the first main oil gallery 71, a second hydraulic oil inlet v2 is provided on the second main oil gallery 72, and the second hydraulic oil inlet v2 serves as an oil return port when the first hydraulic oil inlet v1 takes oil; accordingly, when the hydraulic oil is fed from the second hydraulic oil inlet v2, the first hydraulic oil inlet v1 serves as an oil return port.
Taking the first hydraulic oil inlet v1 as an example, when a swing action is performed, hydraulic oil enters from the first hydraulic oil inlet v1, a part of the hydraulic oil enters the working oil inlet of the hydraulic motor through the first check valve 32 in the first balance valve 30 along the first main oil gallery 71, the hydraulic motor needs a sufficient oil pressure to start the hydraulic motor, but another part of the hydraulic oil enters the first oil inlet 51 of the first relief valve 50, if the set pressure of the first relief valve 50 is low, the first relief valve 50 is easily opened by the oil pressure of the first oil inlet 51, the hydraulic oil entering from the first hydraulic oil inlet v1 easily returns from the first oil outlet 52 of the first relief valve 50, and the oil pressure for opening the hydraulic motor is insufficient, so that when the swing action is performed, in order to prevent the first relief valve 50 from opening, the first relief valve 50 needs a high set pressure. Since the second hydraulic fluid inlet v2 also serves as an oil inlet, the second relief valve 60 also requires a higher set pressure.
However, when the first and second relief valves 50 and 60 both have a high set pressure, and the swing motion is stopped, the first hydraulic oil inlet v1 no longer takes oil, and hydraulic oil comes out from the oil return port of the hydraulic motor, and returns to the second hydraulic oil inlet v2 via the second main oil gallery 72. At this time, in order to soften the swing mechanism when the swing is stopped, it is desirable that the second relief valve 60 is opened to achieve pressure buffering when the hydraulic oil passes through the second oil inlet 61 of the second relief valve 60, and if the second relief valve 60 has a high set pressure, the second relief valve is not easily opened during oil return, so that the impact applied to the swing mechanism when the swing operation is stopped is excessive, and therefore, the second relief valve 60 needs to have a low set pressure when the swing is stopped.
In summary, the arrangement of the relief valve needs to realize "high-pressure starting and low-pressure braking", but the set pressure values of the relief valve in the existing balance valve group are contradictory.
Therefore, in order to solve the above problem, the utility model provides a gyration balanced valve and gyration hydraulic system, the overflow valve has the outer accuse mouth of overflow valve, just the outer accuse mouth of overflow valve is linked together with the pressure spring in the overflow valve, the outer accuse mouth of overflow valve through the pressure boost oil duct with the shuttle valve export intercommunication of shuttle valve. When the swing mechanism is started, taking the first main oil duct as an oil inlet duct as an example, a part of hydraulic oil flows from the first auxiliary working oil port to the first main working oil port along the first main oil duct, finally enters the oil inlet of the hydraulic motor, and the other part of hydraulic oil flows to the first overflow port of the overflow valve; meanwhile, when the slewing mechanism stops, the first main oil duct does not feed oil, the second main oil duct is used as an oil return duct, when hydraulic oil passes through the second overflow port of the overflow valve, because the pressurizing oil duct does not feed the hydraulic oil of the overflow valve, the opening pressure of the overflow valve is the set elastic force of the pressure spring, the overflow valve is easy to open during oil return, the softness when the slewing action stops can be improved, and the impact on the slewing balance valve is reduced.
In order to make the above objects, features and advantages of the present invention more comprehensible, embodiments of the present invention are described in detail below with reference to the accompanying drawings.
Referring to fig. 2, a rotary balanced valve 100 includes:
a shuttle valve 200, the shuttle valve 200 having a first shuttle valve inlet 201, a second shuttle valve inlet 202, and a shuttle valve outlet 203;
a first balance valve 310, the first balance valve 310 having a first main working port a1 and a first sub working port B1;
a second balance valve 320, the second balance valve 320 having a second main working port a2 and a second sub working port B2;
the overflow valve 400 comprises a first overflow port 401, a second overflow port 402 and an overflow valve external control port 403, wherein a pressure spring is arranged in the overflow valve, and the overflow valve external control port 403 is communicated with the pressure spring;
the oil passage comprises a first main oil passage X, a second main oil passage Y and a pressurization oil passage 210, the first main oil passage X is communicated with the first shuttle valve inlet 201, the first auxiliary working oil port B1, the first main working oil port A1 and the first overflow port 401, the second main oil passage Y is communicated with the second shuttle valve inlet 202, the second auxiliary working oil port B2, the second main working oil port A2 and the second overflow port 402, and the pressurization oil passage 210 is connected with the shuttle valve outlet 203 and the overflow valve external control port 403.
In this embodiment, the rotary balance valve 100 further includes a first hydraulic oil inlet V1, a second hydraulic oil inlet V2, a first hydraulic oil outlet C1, and a second hydraulic oil outlet C2, the first hydraulic oil inlet V1 and the first hydraulic oil outlet C1 are disposed on the first main oil gallery X, the first hydraulic oil inlet V1 is connected to a first sub-working oil port B1 and a first shuttle valve inlet 201, and the first hydraulic oil outlet C1 is connected to a first main working oil port a1 and a first overflow port 401; the second hydraulic oil inlet V2 and the second hydraulic oil outlet C2 are arranged on the second main oil gallery Y, the second hydraulic oil inlet V2 is connected with the second auxiliary working oil port B2 and the second shuttle valve inlet 202, and the second hydraulic oil outlet C2 is connected with the second main working oil port A2 and the second overflow port 402.
In this embodiment, the rotary balance valve 100 can operate in two directions, and when the first hydraulic oil inlet V1 is used as an oil inlet, the second hydraulic oil inlet V2 is used as an oil return port; correspondingly, when the second hydraulic oil inlet V2 is an oil inlet, the first hydraulic oil inlet V1 is an oil return port.
In this embodiment, the first balance valve 310 includes a first pressure valve 311 and a first check valve 312, the first pressure valve 311 has a first main working port a1 and a first sub working port B1, one end of the first check valve 312 is connected to the first main working port a1, and the other end is connected to the first sub working port B1; the second balance valve 320 includes a second pressure valve 321 and a second check valve 322, the second pressure valve 321 has a first main working oil port a2 and a first sub working oil port B2, and one end of the second check valve 322 is connected to the second main working oil port a2, and the other end is connected to the second sub working oil port B2.
In this embodiment, the first pressure valve 311 further has a first control port M1 and a first load port N1, and the second pressure valve 322 further has a second control port M2 and a second load port N2.
In this embodiment, the oil passage further includes: the first load oil passage 511 is connected with the first load oil port N1 and the first main working oil port a1, and the second load oil passage 512 is connected with the second load oil port N2 and the second main working oil port a 2.
In this embodiment, the oil passage further includes: the first control oil port M1 is connected to the second control oil port M2 through the first branch oil passage 521, the first sub-working oil port B1 is connected to the second sub-working oil port B2 through the second branch oil passage 522, the connection oil passage 530 is disposed between the first branch oil passage 521 and the second branch oil passage 522, a first end of the connection oil passage 530 is located on the first branch oil passage 521, and a second end of the connection oil passage 530 is located on the second branch oil passage 522.
In this embodiment, the rotary balance valve 100 further includes a first damping member 531 and a second damping member 532, the first damping member 531 and the second damping member 532 are disposed on the second branch oil passage 522, the first damping member 531 is located between the second end of the connection oil passage 530 and the first sub-operation oil port B1, and the second damping member 532 is located between the second end of the connection oil passage 530 and the second sub-operation oil port B2.
In this embodiment, by providing the first damping member 531 and the second damping member 532, the actual pilot ratio of the double balanced valve group of the first balanced valve 310 and the second balanced valve 320 can be reduced, which is beneficial to improving the stability of the operation of the double balanced valve group.
In this embodiment, the first check valve 312 communicates the oil path from the first sub-port B1 to the first main port a 1. The hydraulic oil at the first sub-working port B1 is delivered to the first main working port a1 through the first check valve 312.
In this embodiment, the second check valve 322 connects the second sub-working port B2 to the oil passage of the second main working port a 2. Since the second single valve 322 is unidirectionally conducted, the oil path from the hydraulic oil at the second main working port a2 to the second sub working port B2 through the second check valve 322 is blocked.
In this embodiment, the second pressure valve 321 has a second open position and a second closed position, and the second pressure valve 321 is switched from the second closed position to the second open position, so that the oil path from the hydraulic oil at the second main working port a2 to the second sub working port B2 can be communicated. Two ways of switching the second pressure valve 321 from the second closed position to the second open position are described in detail below.
The first mode is as follows: the second load port N2 has a second spool opening oil pressure, and the second pressure valve 321 is switched from a second closed position to a second open position when the oil pressure at the second load port N2 reaches the second spool opening oil pressure. Specifically, the fluid warp of second main working fluid port a2 department the second load oil duct 512 carry extremely the second load oil port N2, work as the fluid that the second main working fluid port a2 department carried makes the oil pressure of second load oil port N2 reaches when the oil pressure is opened to the second valve core, second pressure valve 221 is switched to the second by the second closed position and is opened the position, second main working fluid port a2 extremely the oil circuit intercommunication of second vice working fluid port B2, the fluid warp of second main working fluid port a2 department the second pressure valve 321 carry extremely the vice working fluid port B2 of second.
The second mode is as follows: the second control port M2 has a second pilot opening oil pressure, and when the oil pressure of the second control port M2 reaches the second pilot opening oil pressure, the second pressure valve 321 is switched from a second closed position to a second open position. Specifically, the oil at the first sub-working oil port B1 is delivered to the second end of the connecting oil passage 530 through the second branch oil passage 522, and then the oil is delivered to the first end of the connecting oil passage 530 along the connecting oil passage 530 and is delivered to the second control oil port M2 from the first end along the first branch oil passage 521. When the oil pressure of the second control oil port M2 reaches the second pilot opening oil pressure by the oil liquid conveyed from the first sub-working oil port B1, the second pressure valve 321 is switched to the second opening position from the second closing position, the second main working oil port a2 is communicated with the oil passage of the second sub-working oil port B2, and the oil liquid at the second main working oil port a2 is conveyed to the second sub-working oil port B2 through the second pressure valve 321.
When the second mode is separately adopted so that the second pressure valve 321 is switched from the second closed position to the second open position, the minimum value of the oil pressure at the first sub-hydraulic port B1 is the first pilot oil pressure. When the oil pressure of the second control port M2 is the second pilot opening oil pressure, the oil pressure at the first sub-hydraulic port B1 is the first pilot oil pressure.
The actual pilot ratio of the double balanced valve group consisting of the first balanced valve 310 and the second balanced valve 320 is the ratio of the second spool opening oil pressure to the first pilot oil pressure.
The geometric pilot ratio of the double-balance valve group is the ratio of the opening oil pressure of the second valve core to the opening oil pressure of the second pilot.
In this embodiment, since the second branch oil passage 522 is provided with the first damping member 531 and the second damping member 532, a part of the hydraulic oil at the first sub-hydraulic oil port B1 is sequentially delivered to the second control oil port M2 along the second branch oil passage 522, the first damping member 531, the connecting oil passage 530, and the first branch oil passage 521. After passing through the first damping member 531, the other part of the hydraulic oil still flows to the second sub-working port B2 through the second damping member 532 along the second branch oil passage 522, and is returned by the second hydraulic oil inlet V2. The oil pressure at the first sub-working port B1 is higher than the oil pressure at the second control port M2. When the oil pressure of the second control port M2 is the second pilot-on oil pressure, the oil pressure at the first sub-working port B1 is higher than the second pilot-on oil pressure, that is, the first pilot oil pressure is higher than the second pilot-on oil pressure, so that the first pilot oil pressure can be increased.
In this embodiment, the first damping member 531 and the second damping member 532 can split and reduce the pressure of the hydraulic oil, and the oil pressure at the first sub-operating port B1 and the oil pressure at the second control port M2 can be maintained at a certain ratio, that is, the ratio of the first pilot oil pressure to the second pilot opening oil pressure, and the ratio at this time satisfies:
second pilot opening oil pressure/first pilot oil pressure ═ alpha4/(α4+β4)；
Wherein α is a diameter of the first damping member 531; β is the diameter of the second damping member 532.
In this embodiment, the diameter of the second damping member 532 is equal to the diameter of the first damping member 531, and the damping coefficient of the second damping member 532 is equal to the damping coefficient of the first damping member 531.
By adjusting the damping coefficients of the first damping member 531 and the second damping member 532, the actual pilot ratio of the double-balanced valve group, that is, the ratio of the first pilot oil pressure to the second pilot opening oil pressure can be adjusted, so that the ratio of the actual pilot ratio to the geometric pilot ratio is α4/(α4+β4) Therefore, the actual pilot ratio is reduced, the difficulty of opening the second balance valve during the swing operation is increased, and the operation stability of the swing balance valve 100 is improved.
In this embodiment, with reference to fig. 2, the rotary balance valve group 100 further includes a spare oil passage (not labeled), a first end of the spare oil passage is connected to the shuttle valve outlet 203, a second end of the spare oil passage is connected to a second end of the connecting oil passage 530, a plug 204 is disposed on the spare oil passage, the plug 204 is in a disconnected state, and hydraulic oil cannot pass through the spare oil passage, so that an actual pilot ratio of the double balance valve group can be adjusted by using the first damping member and the second damping member.
In other embodiments, the actual pilot ratio of the double balanced valve pack may be adjusted without the use of first and second damping members. The spare oil passage is communicated by opening the plug 204, and the first damping member 531 and the second damping member 532 are closed, so that the hydraulic oil directly flows to the first shuttle valve inlet 201 after entering from the first hydraulic oil inlet V1, and then flows to the second control oil port M2 through the shuttle valve outlet 203, and since the first hydraulic oil inlet V1 is also connected with the first sub-working oil port B1, the oil pressure at the first sub-working oil port B1 is the same as the oil pressure at the shuttle valve outlet 203, which is equivalent to the first sub-working oil port B1 being connected with the second control oil port M2; when the hydraulic oil enters from the second hydraulic oil inlet V2, the second sub-working oil port B2 is connected to the first control oil port M1.
With reference to fig. 2, in this embodiment, the relief valve 400 is a single relief valve, the relief valve 400 is a two-way relief valve, and a single valve body of the two-way relief valve has a two-way relief function.
Referring to fig. 6, the two-way relief valve includes: the overflow valve comprises a valve seat 610 and a sleeve 620, wherein a valve cavity, a first overflow port 401, a second overflow port 402 and an overflow valve outer control port 403 are arranged on the valve seat 610; the valve core 630 is disposed in the valve cavity, the valve core 630 includes a main body 631, a first protrusion 632 disposed at one end of the main body 631, and a second protrusion 633 disposed at the other end of the main body 631, and the first protrusion 632 is used for blocking the first overflow port 401.
In this embodiment, the valve core 630 can move in the axial direction of the valve cavity to close or open the oil passages of the first overflow port 401 and the second overflow port 402, the first overflow port 401 is disposed on the bottom surface of the valve seat 610, and the second overflow port 402 is disposed on the side wall of the valve seat 610.
In this embodiment, the diameter of the main body 631 is larger than the diameters of the first protrusion 632 and the second protrusion 633, the main body 631 is tightly attached to the inner wall of the valve chamber, a first gap 601 is formed between the first protrusion 632 and the inner wall of the valve chamber, when the first protrusion 632 blocks the first overflow port 401, the second overflow port 402 is communicated with the first gap 601, and the second overflow port 402 is not communicated with the first overflow port 401.
In this embodiment, when oil enters the first overflow port 401, after the oil pressure reaches the set pressure value of the two-way overflow valve, the hydraulic oil pushes the bottom of the first protrusion 632 to move the valve core 630 upward, after the valve core 630 moves upward, the first overflow port 401 is communicated with the second overflow port 402, and the hydraulic oil flows out from the second overflow port 402; when oil enters the second overflow port 402, hydraulic oil enters a first gap 601 between the first protrusion 632 and the inner wall of the valve cavity, the hydraulic oil acts on the side wall of the first protrusion 632, the valve core 630 can be pushed to move upwards after the oil pressure reaches a set pressure, the first overflow port 401 is opened after the valve core 630 moves upwards, the first overflow port 401 is communicated with the second overflow port 402, and the hydraulic oil flows out from the first overflow port 401, so that bidirectional overflow can be realized by a single valve body.
In this embodiment, a sealing ring 603 is further disposed between the main body 631 and the valve cavity.
In this embodiment, the first protrusion 632 is a tapered protrusion, the tapered protrusion is tapered in a direction approaching the first overflow port 401, and a portion of the tapered protrusion is inserted into the first overflow port 401 to close the first overflow port 401.
With continued reference to FIG. 6, a second clearance 602 is provided between the second protrusion 633 and the inner wall of the valve chamber, and the relief valve outer control port 403 communicates with the second clearance 602.
In this embodiment, the hydraulic oil may enter the second clearance 602 from the spill valve external control port 403, and the hydraulic oil acts on the second bump 633 to apply a downward force to the valve element 630, which is opposite to the direction of the force applied to the valve element 630 by the hydraulic oil entering from the first spill port 401 or the second spill port 402.
With continued reference to fig. 6, an adjustment rod 641 is coupled to the top of the sleeve 620, and the pressure spring 642 is disposed between the adjustment rod 641 and the second bump 633 of the valve core 630.
In this embodiment, a bonnet 640 is connected to the top of the sleeve 620, and the adjusting rod 641 is connected to the bonnet 640; in other embodiments, the top of the sleeve 620 may be provided without a bonnet.
In this embodiment, the pressure spring 642 abuts against the second protrusion 633 through the sliding block 643, the pre-compression amount of the pressure spring 642 is adjusted through the adjusting rod 641, and the elasticity of the pressure spring 642 causes the valve core 630 to abut against the step 644 provided at the first overflow port 401, so as to close the first overflow port 401.
Generally, when the oil pressure of the first overflow port 401 or the second overflow port 402 overcomes the elastic force of the pressure spring 642, the valve core 630 is driven to move upwards, and the second overflow port 402 or the first overflow port 401 is opened to overflow. However, in the present embodiment, when the swing mechanism starts to operate, taking the first hydraulic oil inlet V1 as an oil inlet as an example, hydraulic oil enters the relief valve 400 from the first overflow port 401, and because the supercharging oil passage 210 is provided, a part of hydraulic oil enters the second gap 602 from the relief valve external control port 403 through the supercharging oil passage 210, in this case, the opening pressure of the relief valve 400 is not only the elastic force of the pressure spring 642, but also the sum of the elastic force of the pressure spring 642 and the acting force of the oil at the relief valve external control port 403; when the swing mechanism stops operating, hydraulic oil returns from the second overflow port 402, and at this time, because oil does not enter the overflow valve outer control port 403 any more, the opening pressure of the overflow valve 400 is the elastic force of the pressure spring 642.
By arranging the supercharging oil passage 210, the pressure spring 642 can set a smaller elastic force, and when the swing mechanism is started, the additional hydraulic oil acting force is added at the position of the outer control port 403 of the overflow valve, so that the opening pressure of the overflow valve 400 is increased, and the situation that the swing mechanism cannot act because the overflow valve 400 is opened when the swing mechanism is started can be prevented; meanwhile, when the rotation action is stopped, the opening pressure of the overflow valve 400 is the set elastic force of the pressure spring 642, so that the overflow valve 400 can be easily opened during oil return, the softness of the rotation mechanism during stop is improved, and overlarge impact is avoided, thereby really realizing high-pressure start and low-pressure brake.
With continued reference to fig. 2, in this embodiment, the rotary balance valve 100 further includes a brake port Br, and the brake port Br is connected to the shuttle valve outlet 203 of the shuttle valve 200, and is used for connecting a brake.
Referring to fig. 3, in the present embodiment, the swing balancing valve 100 further includes: a first relief valve 110 and a second relief valve 120, the first relief valve 110 having a first relief valve inlet 111 and a first relief valve outlet 112, the second relief valve 120 having a second relief valve inlet 121 and a second relief valve outlet 122, the first relief valve inlet 111 and the second relief valve outlet 122 being connected on the first main working oil passage X between the first hydraulic oil inlet V1 and the first sub working oil port B1, the first relief valve outlet 112 and the second relief valve inlet 121 being connected on the second main oil passage Y between the second hydraulic oil inlet V2 and the second sub working oil port B2.
In this embodiment, the first safety valve 110 is used for opening the first safety valve 110 when the oil pressure of the oil fed from the first hydraulic oil inlet V1 is too large, and the hydraulic oil returns through the first safety valve outlet 112 of the first safety valve 110, so as to prevent other hydraulic components from being damaged due to too large oil pressure; the second relief valve 120 is used for opening the second relief valve 120 when the oil pressure fed from the second hydraulic oil inlet V2 is too large, and the hydraulic oil returns through the second relief valve outlet 122 of the second relief valve 120, so as to prevent other hydraulic components from being damaged due to the too large oil pressure.
Referring to fig. 4, in another embodiment, the relief valve 400 is provided in plurality, and the relief valve 400 includes a first relief valve 410 and a second relief valve 420, and the first relief valve 410 and the second relief valve 420 are connected in anti-parallel between the first main gallery X and the second main gallery Y.
In this embodiment, the first relief valve 410 includes: a first overflow inlet 411, a first overflow outlet 412, and a first overflow valve external control port 413; the second relief valve 420 includes: a second overflow inlet 421, a second overflow outlet 422, and a second overflow valve external control port 423, wherein the first overflow inlet 411 and the second overflow outlet 422 are connected to the first overflow port 401, the first overflow outlet 412 and the second overflow inlet 421 are connected to the second overflow port 402, and the first overflow valve external control port 413 and the second overflow valve external control port 423 are connected to the overflow valve external control port 403.
Two overflow valves which are connected in parallel in an opposite direction are adopted, for example, oil is fed from a first hydraulic oil inlet V1, when the slewing mechanism runs, hydraulic oil enters from the first hydraulic oil inlet V1, and a part of hydraulic oil flows to a working oil port of the hydraulic motor through a first main oil gallery X and is used for driving the hydraulic motor to rotate; a part of hydraulic oil flows to the shuttle valve 200 through the first shuttle valve inlet 201, the second shuttle valve inlet 202 is closed, and flows to the overflow valve external control port 403 from the shuttle valve outlet 203 through the pressurization oil duct 210, because the first overflow valve external control port 413 and the second overflow valve external control port 423 are both connected to the overflow valve external control port 403, the hydraulic oil in the pressurization oil duct 210 flows to the first overflow valve 410 through the first overflow valve external control port 413, and flows to the second overflow valve 420 through the second overflow valve external control port 423, so as to increase the pressure for opening the first overflow valve 410 and the second overflow valve 420, and prevent the first overflow valve 410 from opening to cause the swing mechanism to be unable to normally operate when the swing mechanism operates.
When the rotation action is stopped, the first hydraulic oil inlet V1 does not feed oil any more, hydraulic oil flows from the oil return port of the hydraulic motor to the second hydraulic oil outlet C2 through the second main oil passage Y for oil return, when the hydraulic oil passes through the second overflow inlet 421 of the second overflow valve 420, the second overflow valve 420 can be opened when the oil pressure is greater than the elastic force set by the pressure spring of the second overflow valve 420, so that the hydraulic oil flows to the first hydraulic oil outlet C1 through the second overflow outlet 422 for oil return, and the impact on the rotation mechanism when the rotation mechanism is stopped can be reduced.
Similarly, when the second hydraulic fluid inlet V2 is used as a fluid inlet, the second relief valve 420 is prevented from opening during the swing operation, and the first relief valve 410 can be easily opened to perform relief when the swing operation is stopped.
The embodiment of the present invention further provides a rotary hydraulic system 700, which includes the rotary balance valve 100 as described above.
Referring to fig. 5, the swing hydraulic system 700 further includes: a hydraulic motor 710, wherein the hydraulic motor 710 has a first working port 711 and a second working port 712, the first working port 711 is connected to a first main working port a1 and a first overflow port 401 on the first main oil gallery X, and the second working port 712 is connected to a second main working port a2 and a second overflow port 402 on the second main oil gallery Y; a brake 720, wherein the brake 720 is used for braking the hydraulic motor 710, the brake 720 comprises an oil inlet 721, and the oil inlet of the brake 720 is connected with the shuttle valve outlet 203 of the shuttle valve 200.
In this embodiment, specifically, the first working port 711 of the hydraulic motor 710 is connected to the first hydraulic oil outlet C1, and the second working port 712 is connected to the second hydraulic oil outlet C2.
In this embodiment, specifically, the oil inlet 721 of the brake 720 is connected to the brake port Br.
In this embodiment, the swing hydraulic system further includes: reversing valve 730, reversing valve 730 has first working port W1 and second working port W2, first working port W1 with first hydraulic oil entry V1 is connected, second working port W2 with second hydraulic oil entry V2 is connected, through reversing valve 730 realizes that the oil feed between first hydraulic oil entry V1 and the second hydraulic oil entry V2 switches.
In this embodiment, the direction valve 730 further includes: the hydraulic system comprises a pressure port P and an oil tank port T, wherein the pressure port P is connected with an oil pump and used for providing hydraulic oil for the rotary hydraulic system 700; and the oil tank port T is used as an oil drainage port and is connected with an oil tank.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one of ordinary skill in the pertinent art without departing from the scope or spirit of the present invention, and the scope of the present invention is defined by the appended claims.
Claims (12)
1. A rotary balanced valve comprising:
a shuttle valve having a first shuttle valve inlet, a second shuttle valve inlet, and a shuttle valve outlet;
a first balance valve having a first main working port and a first sub working port;
a second balanced valve having a second main working port and a second sub working port;
the overflow valve comprises a first overflow port, a second overflow port and an overflow valve external control port, a pressure spring is arranged in the overflow valve, and the overflow valve external control port is communicated with the pressure spring;
the oil duct comprises a first main oil duct, a second main oil duct and a pressurizing oil duct, the first main oil duct is communicated with the first shuttle valve inlet, the first auxiliary working oil port, the first main working oil port and the first overflow port, the second main oil duct is communicated with the second shuttle valve inlet, the second auxiliary working oil port, the second main working oil port and the second overflow port, and the pressurizing oil duct is communicated with the shuttle valve outlet and the overflow valve external control port.
2. The rotary balanced valve of claim 1, wherein the relief valve is a two-way relief valve when the relief valve is single, the two-way relief valve comprising:
the valve comprises a valve seat and a sleeve, wherein the valve seat is provided with a valve cavity, a first overflow port, a second overflow port and an overflow valve external control port;
the valve core is arranged in the valve cavity and comprises a main body, a first bulge arranged at one end of the main body and a second bulge arranged at the other end of the main body, and the first bulge is used for plugging the first overflow port.
3. The rotary balanced valve of claim 2, wherein the diameter of the main body is larger than the diameters of the first protrusion and the second protrusion, the main body is tightly attached to the inner wall of the valve chamber, a first gap is formed between the first protrusion and the inner wall of the valve chamber, and when the first protrusion blocks the first overflow port, the first gap is communicated with the second overflow port;
and a second clearance is formed between the second bulge and the inner wall of the valve cavity, and the outer control port of the overflow valve is communicated with the second clearance.
4. The rotary balance valve of claim 3 wherein an adjustment stem is attached to the top of the sleeve, and the pressure spring is disposed between the adjustment stem and the second protrusion of the valve spool.
5. The rotary balance valve of claim 1 wherein the plurality of relief valves includes a first relief valve and a second relief valve, and the first relief valve and the second relief valve are connected in anti-parallel between the first main gallery and the second main gallery.
6. The slew balanced valve of claim 5, where the first spill valve comprises a first spill inlet, a first spill outlet, and a first spill valve outer control port, where the second spill valve comprises a second spill inlet, a second spill outlet, and a second spill valve outer control port, where the first spill inlet and the second spill outlet are connected to the first spill port, where the first spill outlet and the second spill inlet are connected to the second spill port, and where the first spill valve outer control port and the second spill valve outer control port are connected to the spill valve outer control port.
7. The rotary balanced valve of claim 1, wherein the first balanced valve comprises a first pressure valve and a first check valve, the first pressure valve has a first main working port and a first sub working port, one end of the first check valve is connected to the first main working port, and the other end of the first check valve is connected to the first sub working port;
the second balance valve comprises a second pressure valve and a second check valve, the second pressure valve is provided with a second main working oil port and a second auxiliary working oil port, one end of the second check valve is connected with the second main working oil port, and the other end of the second check valve is connected with the second auxiliary working oil port.
8. The rotary balance valve of claim 7, wherein the first pressure valve has a first control oil port, the second pressure valve has a second control oil port, the first control oil port is connected with the second control oil port through a first branch oil passage, the first sub-working oil port is connected with the second sub-working oil port through a second branch oil passage, a connecting oil passage is further provided between the first branch oil passage and the second branch oil passage, a first end of the connecting oil passage is located on the first branch oil passage, and a second end of the connecting oil passage is located on the second branch oil passage;
the rotary balance valve further comprises a first damping part and a second damping part, and the first damping part is positioned on the second branch oil passage between the second end of the connecting oil passage and the first auxiliary working oil port; the second damping piece is located between the second end of the connecting oil duct and the second auxiliary working oil port on the second branch oil duct.
9. The rotary balance valve of claim 8 wherein the damping coefficient of the second damping member is equal to the damping coefficient of the first damping member.
10. The rotary balance valve of claim 7 wherein the first pressure valve has a first control port and the second pressure valve has a second control port, the first secondary working port is connected to the second control port through a first branch oil passage and the second secondary working port is connected to the first control port through a second branch oil passage.
11. A swing hydraulic system comprising a swing balancing valve according to any one of claims 1 to 10.
12. The swing hydraulic system as claimed in claim 11, further comprising:
the hydraulic motor is provided with a first working port and a second working port, the first working port is connected with a first main working oil port and a first overflow port on the first main oil duct, and the second working port is connected with a second main working oil port and a second overflow port on the second main oil duct;
the brake is used for braking the hydraulic motor and comprises an oil inlet, and the oil inlet of the brake is connected with the shuttle valve outlet of the shuttle valve.
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| CN202021673950.8U CN212337750U (en) | 2020-08-12 | 2020-08-12 | Rotary balance valve and rotary hydraulic system |
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| CN202021673950.8U CN212337750U (en) | 2020-08-12 | 2020-08-12 | Rotary balance valve and rotary hydraulic system |
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113883109A (en) * | 2021-09-22 | 2022-01-04 | 上海中联重科桩工机械有限公司 | Engineering machinery control device and engineering machinery |
| CN114076127A (en) * | 2020-08-12 | 2022-02-22 | 上海伦联机电设备有限公司 | Rotary balance valve and rotary hydraulic system |
| CN114321049A (en) * | 2021-12-27 | 2022-04-12 | 广东碧品居建筑工业化有限公司 | Hydraulic oil cylinder control device and hydraulic system |
| CN115263843A (en) * | 2022-07-21 | 2022-11-01 | 燕山大学 | Rotary buffer valve for improving stability of rotary system and working method thereof |
| CN115434973A (en) * | 2022-08-22 | 2022-12-06 | 贵阳海之力液压有限公司 | Overflow balance valve and EHA hydraulic circuit using same |
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2020
- 2020-08-12 CN CN202021673950.8U patent/CN212337750U/en active Active
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114076127A (en) * | 2020-08-12 | 2022-02-22 | 上海伦联机电设备有限公司 | Rotary balance valve and rotary hydraulic system |
| CN114076127B (en) * | 2020-08-12 | 2024-06-21 | 上海伦联机电设备有限公司 | Rotary balance valve and rotary hydraulic system |
| CN113883109A (en) * | 2021-09-22 | 2022-01-04 | 上海中联重科桩工机械有限公司 | Engineering machinery control device and engineering machinery |
| CN114321049A (en) * | 2021-12-27 | 2022-04-12 | 广东碧品居建筑工业化有限公司 | Hydraulic oil cylinder control device and hydraulic system |
| CN115263843A (en) * | 2022-07-21 | 2022-11-01 | 燕山大学 | Rotary buffer valve for improving stability of rotary system and working method thereof |
| CN115434973A (en) * | 2022-08-22 | 2022-12-06 | 贵阳海之力液压有限公司 | Overflow balance valve and EHA hydraulic circuit using same |
| CN115434973B (en) * | 2022-08-22 | 2024-06-04 | 贵阳海之力液压有限公司 | Overflow balance valve and EHA hydraulic circuit using same |
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