CN216190493U - Double-fixed displacement pump converging multi-way valve - Google Patents
Double-fixed displacement pump converging multi-way valve Download PDFInfo
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- CN216190493U CN216190493U CN202122325379.1U CN202122325379U CN216190493U CN 216190493 U CN216190493 U CN 216190493U CN 202122325379 U CN202122325379 U CN 202122325379U CN 216190493 U CN216190493 U CN 216190493U
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Abstract
A double constant delivery pump confluence multi-way valve relates to the hydraulic technical field of a straight-arm lorry-mounted crane. The system comprises a first pump oil inlet control unit, a proportional reversing valve working unit, a confluence control unit, a rotary reversing unit and a second pump oil inlet control unit; the first pump oil inlet control unit is connected with the first quantitative oil pump and supplies oil to the working unit of the proportional reversing valve, the second pump oil inlet control unit is connected with the second quantitative oil pump and supplies oil to the rotary reversing unit, when the rotary reversing unit does not work, the second quantitative oil pump and the first quantitative oil pump are converged through the check valve and the hydraulic control reversing valve of the confluence control unit, and the two pumps simultaneously supply oil to the working unit of the proportional reversing valve, so that the working efficiency is improved; when the rotary reversing union works, a hydraulic control reversing valve of the confluence control union cuts off a confluence channel of the second quantitative oil pump and the first quantitative oil pump, and the second quantitative oil pump independently supplies oil to the rotary reversing union, so that rotary action flow matching is realized, and energy consumption and system temperature rise are reduced.
Description
Technical Field
The utility model relates to the technical field of hydraulic pressure of straight-arm lorry-mounted cranes, in particular to a confluence multi-way valve with double constant delivery pumps.
Background
The straight arm lorry-mounted crane is a multipurpose machine which is arranged on an automobile chassis and can load and unload heavy objects in a certain range, has the characteristics of quickness, flexibility, convenience and integration of hoisting and transportation, and is widely applied to the fields of hoisting and transportation such as equipment loading and unloading, landscaping, municipal construction and the like. In recent years, with the development of markets and technologies, the times of concepts such as high efficiency, high speed, energy conservation and the like are becoming the technical development trend of lorry-mounted cranes.
The main operation actions of the straight-arm lorry-mounted crane comprise stretching, winding, amplitude variation and rotation, and the multi-way valve for getting on the crane is a core element of the hydraulic action control systems. At present, a single oil pump oil supply and proportional multi-way valve control system is adopted in a main stream of a straight boom lorry-mounted crane, requirements for system flow and pressure are greatly different due to main operation actions of the straight boom crane, an existing single pump oil supply system cannot meet requirements for high efficiency, low energy consumption and accurate control, and meanwhile, due to the limitation of the power characteristics of a chassis engine, a large-displacement single pump system cannot solve the problem of engine pressure-holding flameout under high load pressure.
The utility model patent application number 202010424973.3 discloses a confluence proportion multi-way reversing valve for a straight-arm lorry-mounted crane and a working method, load pressure signals are collected from two output working oil ports of the reversing valve of a winch linkage, a multi-way valve device and a working method that a first oil pump and a second oil pump are confluent and the rest states are not confluent during the winch action are adopted, the double-pump confluence during the winch action can only be realized, the pressure of two sides where the first pump and the second pump are located is the same, otherwise, when the set pressure of one side of a slewing linkage is low, the LS oil circuit pressure of one side of the winch linkage in the confluence state is pulled down by the pressure of one side of the slewing linkage, and the pressure of the whole system in the confluence state is not available; when the pressure settings on the hoisting connection side and the rotation connection side are both high enough, the engine on the engine chassis may be blocked and flamed out due to insufficient output power or torque.
The utility model patent application number 2017109447089.6 discloses a multi-way valve reversing device of a lorry-mounted crane, which relates to a switch-type multi-way valve instead of a proportional core multi-way valve, the working connection of the multi-way valve can not be subjected to any composite operation, the action override performance, the flow matching performance and the energy consumption are poor, and the requirements of the technical development of the lorry-mounted crane product at the present stage can not be met.
SUMMERY OF THE UTILITY MODEL
Aiming at the problems, the utility model provides the double-fixed displacement pump confluence multi-way valve which has high action efficiency of the straight-arm lorry-mounted crane and can avoid engine pressure build-up flameout and stable rotation action when in confluence under the rotation linkage operation state.
The technical scheme of the utility model is as follows: the double constant delivery pump confluence multi-way valve is characterized by comprising a first pump oil inlet control link, a proportional reversing valve working link, a confluence control link, a rotary reversing link and a second pump oil inlet control link;
the first pump oil inlet control communication supplies oil to the working communication of the proportional reversing valve through a first quantitative oil pump;
the second pump oil inlet control communication is communicated with a second quantitative oil pump to supply oil to the rotary reversing union;
the confluence control joint is arranged between the first pump oil inlet control joint and the second pump oil inlet control joint and is used for controlling the confluence of the first quantitative oil pump and the second quantitative oil pump;
the confluence control union comprises a hydraulic control reversing valve and a shuttle valve;
the rotary reversing union controls the connection and disconnection of a confluence channel of a first quantitative oil pump and a second quantitative oil pump through the hydraulic control reversing valve, so that the second quantitative oil pump independently supplies oil to the rotary reversing union when the rotary reversing union is in a working state;
an A4 oil port and a B4 oil port of the rotary reversing linkage are respectively connected with working oil ports on two sides of the shuttle valve;
and a middle working oil port of the shuttle valve is communicated with a control oil port of the hydraulic control reversing valve.
The confluence control joint also comprises a fifth damping part;
and the damper five is arranged on a spring cavity oil return path of the hydraulic control reversing valve and used for controlling the reversing action speed of a valve core of the hydraulic control reversing valve.
The rotary reversing joint comprises a rotary reversing valve and a pressure matcher six;
a first working oil port of the rotary reversing valve is communicated with an oil inlet P1 and an oil inlet P2;
a second working oil port of the rotary reversing valve is communicated with an oil return port T1 and an oil return port T2;
the other two working oil ports of the rotary reversing valve are communicated with a sixth pressure matcher;
and two working oil ports of the hydraulic control reversing valve are communicated with a first control oil port and a first working oil port of the pressure matcher, and the communication of the oil ports MLS1 and MLS2 is realized through the oil inlet control linkage of the second pump.
The rotary reversing joint also comprises a first pressure-limiting overflow valve six and a second pressure-limiting overflow valve six;
one end of the first pressure limiting overflow valve six is communicated with an oil return port T2, and the other end of the first pressure limiting overflow valve six is communicated with an A4 working oil port;
one end of the second pressure limiting overflow valve six is communicated with the oil return port T2, and the other end of the second pressure limiting overflow valve six is communicated with the B4 working oil port.
The second pump oil inlet control unit comprises a one-way valve, a pressure switching valve, a damping seventh valve and a three-way flow valve seventh valve;
the oil inlet P2 supplies oil to the rotary reversing union through the one-way valve and is communicated with an oil inlet of the three-way flow valve;
an oil outlet and a damping seventh of the three-way flow valve seventh are respectively communicated with an oil return port T2;
and the load sensitive oil path LS2 is communicated with a spring cavity of the three-way flow valve seventh and a working oil port of the damper seventh through the pressure switching valve.
The first pump oil inlet control unit comprises a three-way flow valve I, a damping I and a load sensitive LS oil path pressure limiting overflow valve;
the LS1 control oil way is communicated with the oil return port T1 through a first damper;
a working oil port I of the three-way flow valve I is communicated with an oil inlet P1, and a working oil port II is communicated with an oil return port T1;
an oil port I of the load-sensitive LS oil path pressure-limiting overflow valve is communicated with an oil return port T1, and an oil port II of the load-sensitive LS oil path pressure-limiting overflow valve is communicated with a load-sensitive oil path pressure measuring oil port MLS 1;
and a control oil port of the first three-way flow valve is connected to a connection oil path between the load-sensitive LS oil path pressure-limiting overflow valve and a load-sensitive oil path pressure-measuring oil port MLS 1.
The working connection of the proportional reversing valve comprises one or the combination of any more of a telescopic reversing connection, a winch reversing connection and a variable amplitude reversing connection.
The telescopic reversing joint comprises a telescopic reversing valve and a pressure matcher II;
a first working oil port of the telescopic reversing valve is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the second pressure matcher is communicated with a first working oil port and the oil inlet control linkage of the second pump;
the telescopic reversing valve is communicated with a second pressure matcher, and the valve port pressure difference of the telescopic reversing valve is controlled through the second pressure matcher so as to realize the proportional control of the telescopic reversing valve.
The winch reversing joint comprises a winch reversing valve and a pressure matcher III;
a first working oil port of the winch reversing valve is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the third pressure matcher is communicated with a first working oil port and a second pump oil inlet control joint;
the winch reversing valve is communicated with the third pressure matcher, and the valve port pressure difference of the winch reversing valve is controlled by the third pressure matcher so as to realize the proportional control of the winch reversing valve.
The variable-amplitude reversing connection comprises a variable-amplitude reversing valve and a pressure matcher IV;
a working oil port I of the variable amplitude reversing valve is communicated with an oil inlet P1, and a working oil port II is communicated with an oil return port T1;
a control oil port of the pressure matcher IV is communicated with a working oil port I and the second pump oil inlet control link;
the variable-amplitude reversing valve is communicated with the pressure matcher IV, and the valve port pressure difference of the variable-amplitude reversing valve is controlled through the pressure matcher IV so as to realize the proportional control of the variable-amplitude reversing valve.
According to the utility model, a first pump oil inlet control unit is connected with a first quantitative oil pump and supplies oil to a working unit of a proportional reversing valve, a second pump oil inlet control unit is connected with a second quantitative oil pump and supplies oil to a rotary reversing unit, when the rotary reversing unit does not work, the second quantitative oil pump and the first quantitative oil pump are converged through a one-way valve and a hydraulic control reversing valve of a confluence control unit, and the two pumps simultaneously supply oil to the working unit of the proportional reversing valve, so that the working efficiency is improved; when the rotary reversing union works, a hydraulic control reversing valve of the confluence control union cuts off a confluence channel of the second quantitative oil pump and the first quantitative oil pump, and the second quantitative oil pump independently supplies oil to the rotary reversing union, so that rotary action flow matching is realized, and energy consumption and system temperature rise are reduced.
A pressure switching valve matched with a one-way valve is arranged between a spring cavity control port of a three-way flow valve seventh of the second pump oil inlet control joint and a load sensitive oil path LS2 of the second oil pump system, so that the second oil pump system can realize different working pressure levels, the system is ensured to be balanced with the output power and the torque of the engine in a confluence state, and the pressure-out flameout phenomenon of the engine during working is avoided. The other function of the check valve is to prevent the hydraulic impact of the first oil pump system from being transmitted to the second oil pump, so that the second quantitative oil pump can adopt an inexpensive medium-pressure gear pump, and the manufacturing cost of the system is reduced.
Drawings
Figure 1 is a hydraulic schematic of the present invention,
in the figure, 1 is a first pump oil inlet control unit, 11 is a three-way flow valve I, 12 is a filter, 13 is a damping I, 14 is a load-sensitive LS oil way pressure-limiting overflow valve, 2 is a telescopic reversing unit, 21 is a telescopic reversing valve, 22 is a pressure matcher II, 23 is a first pressure-limiting overflow valve II, 24 is a second pressure-limiting overflow valve II, 3 is a hoisting reversing unit, 31 is a hoisting reversing valve, 32 is a pressure matcher III, 33 is a first pressure-limiting overflow valve III, 34 is a second pressure-limiting overflow valve III, 4 is a variable amplitude reversing unit, 41 is a variable amplitude reversing valve, 42 is a pressure matcher IV, 43 is a first pressure-limiting overflow valve IV, 44 is a second pressure-limiting overflow valve IV, 5 is a confluence control unit, 51 is a hydraulic control reversing valve, 52 is a damping V, 53 is a shuttle valve, 6 is a rotary reversing unit, 61 is a rotary reversing valve, 62 is a pressure six, 63 is a first pressure-limiting overflow valve VI, 64 is a second pressure-limiting six matcher, 7 is a second pump-in oil control unit, 71 is a one-way valve, 72 is a pressure switching valve, 73 is a damping valve seven, and 74 is a three-way flow valve seven.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
As shown in fig. 1, in the drawing, MLS1 is a load-sensitive oil line pressure measuring oil port MLS1, and MLS2 is a load-sensitive oil line pressure measuring oil port MLS 2; p1 is a first oil supply port, P2 is a second oil supply port; MP1 is the first oil pump pressure port, MP2 is the second oil pump pressure port.
The double constant delivery pump confluence multiway valve comprises a first pump oil inlet control joint 1, a proportional reversing valve working joint, a confluence control joint 5, a rotary reversing joint 6 and a second pump oil inlet control joint 7;
the first pump oil inlet control unit 1 supplies oil to the proportional reversing valve working unit through a first quantitative oil pump;
the second oil pumping control unit 7 supplies oil to the rotary reversing unit 6 through a second quantitative oil pump;
the confluence control joint 5 is arranged between the first pump oil inlet control joint 1 and the second pump oil inlet control joint 7 and is used for controlling the confluence of the first quantitative oil pump and the second quantitative oil pump;
the confluence control union 5 comprises a hydraulic control reversing valve 51 and a shuttle valve 53;
the rotary reversing union 6 controls the on-off of a confluence channel of a first quantitative oil pump and a second quantitative oil pump through the hydraulic control reversing valve 51, so that the second quantitative oil pump independently supplies oil to the rotary reversing union 6 when the rotary reversing union 6 is in a working state;
an A4 oil port and a B4 oil port of the rotary reversing link 6 are respectively connected with working oil ports on two sides of the shuttle valve 53;
and the middle working oil port of the shuttle valve 53 is communicated with the control oil port of the hydraulic control reversing valve 51.
The confluence control unit 5 realizes the synchronous control of the on-off of the main oil paths of the two oil pumps (the first quantitative oil pump and the second quantitative oil pump) and the on-off of the load sensitive signal oil path LS1 (the dotted line connection part between the hydraulic control reversing valve 51 and the MLS1 and the residual right dotted line part is LS2 in fig. 1) and LS2 of the two oil pump systems through the hydraulic control reversing valve 51.
The working oil ports on two sides of the hydraulic control reversing valve 51 are respectively connected with the main oil passages of the first oil pump system and the second oil pump system which are arranged on two sides of the hydraulic control reversing valve in parallel, and the load sensitive signal oil passages LS1 and LS 2. The working oil ports A4 and B4 of the rotary reversing linkage supplied by the second oil pump system are respectively led out of control oil paths and connected to the working oil ports on the two sides of the shuttle valve 53, and the middle working oil port of the shuttle valve 53 is communicated with the control oil port of the hydraulic control reversing valve 51.
The confluence control joint 5 also comprises a damper five 52;
the five damping 52 is arranged on a spring cavity oil return path of the hydraulic control reversing valve 51 and is used for controlling the reversing action speed of a valve core of the hydraulic control reversing valve 51 and avoiding hydraulic reversing impact.
The rotary reversing joint 6 comprises a rotary reversing valve 61 and a pressure matcher six 62;
a first working oil port of the rotary reversing valve 61 is communicated with an oil inlet P1 of the first oil pumping control link 1 and an oil inlet P2 of the second oil pumping control link 7;
a second working oil port of the rotary reversing valve 61 is communicated with an oil return port T1 of the first oil pump oil inlet control joint 1 and an oil return port T2 of the second oil pump oil inlet control joint 7;
the other two working oil ports of the rotary reversing valve 61 are communicated with two working oil ports (a second working oil port and a third working oil port) and a second control port of the pressure matcher six 62;
two working oil ports of the hydraulic control reversing valve 51 are communicated with a first control oil port and a first working oil port of the pressure matcher six 62, and the communication of the oil ports MLS1 and MLS2 is realized through the second pump oil inlet control link 7.
The rotary reversing joint 6 also comprises a first pressure-limiting overflow valve six 63 and a second pressure-limiting overflow valve six 64;
one end of the first pressure limiting overflow valve six 63 is communicated with an oil return port T2, and the other end of the first pressure limiting overflow valve six is communicated with an A4 working oil port;
one end of the second pressure limiting overflow valve six 64 is communicated with the oil return port T2, and the other end of the second pressure limiting overflow valve six 64 is communicated with the B4 working oil port.
The second oil pumping control joint 7 comprises a one-way valve 71, a pressure switching valve 72, a damping seven 73 and a three-way flow valve seven 74;
the oil inlet P2 supplies oil to the rotary reversing joint 6 through the one-way valve 71 and is communicated with an oil inlet of the three-way flow valve seven 74;
an oil outlet of the three-way flow valve seven 74 and the damping seven 73 are respectively communicated with an oil return port T2;
the load-sensitive oil path LS2 is communicated with the spring cavity of the three-way flow valve seven 74 and the working oil port of the damper seven 73 through the pressure switching valve 72.
The three-way flow valve seven 74 is matched with the one-way valve 71 to realize the low-pressure unloading control of the second quantitative oil pump with a set pressure value; the check valve 71 of the main oil way is arranged on the second oil inlet control union 7 of the second quantitative oil pump, so that the oil port of the second quantitative oil pump can not be transmitted by the hydraulic pulse of the first oil pump system in a confluence state, and the manufacturing cost of the system can be further reduced by adopting a medium-pressure gear pump for the second quantitative oil pump.
The first pump oil inlet control unit 1 comprises a three-way flow valve I11, a damping I13 and a load sensitive LS oil path pressure limiting overflow valve 14;
the LS1 control oil way is communicated with the oil return port T1 through a first damper 13;
a first working oil port of the three-way flow valve I11 is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
an oil port I of the load-sensitive LS oil path pressure-limiting overflow valve 14 is communicated with an oil return port T1, and an oil port II of the load-sensitive LS oil path pressure-limiting overflow valve is communicated with a load-sensitive oil path pressure measuring oil port MLS 1;
and a control oil port of the three-way flow valve I11 is connected to a connection oil path between the load-sensitive LS oil path pressure-limiting overflow valve 14 and a load-sensitive oil path pressure-measuring oil port MLS 1.
Further optimized, the first oil pumping control unit 1 further comprises a filter 12 arranged between the pressure measuring oil port MLS1 of the load-sensitive oil path and the first damper 13.
The working connection of the proportional reversing valve comprises one or the combination of any more of a telescopic reversing connection 2, a winch reversing connection 3 and a variable amplitude reversing connection 4.
The telescopic reversing joint 2 comprises a telescopic reversing valve 21 and a second pressure matcher 22;
a first working oil port of the telescopic reversing valve 21 is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the second pressure matcher 22 is communicated with a first working oil port and the second pump oil inlet control connector 7;
the telescopic reversing valve 21 is communicated with a second pressure matcher 22, and the valve port pressure difference of the telescopic reversing valve 21 is controlled through the second pressure matcher 22 so as to realize the proportional control of the telescopic reversing valve 21.
The winch reversing connection 3 comprises a winch reversing valve 31 and a pressure matcher III 32;
a first working oil port of the winch reversing valve 31 is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the third pressure matcher 32 is communicated with a first working oil port and the second pump oil inlet control connector 7;
the winch reversing valve 31 is communicated with a third pressure matcher 32, and the valve port pressure difference of the winch reversing valve 31 is controlled through the third pressure matcher 32 so as to realize the proportional control of the winch reversing valve 31.
The variable amplitude reversing connection 4 comprises a variable amplitude reversing valve 41 and a pressure matcher IV 42;
a first working oil port of the variable amplitude reversing valve 41 is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the pressure matcher IV 42 is communicated with a working oil port I and the second pump oil inlet control joint 7;
the variable-amplitude reversing valve 41 is communicated with a pressure matcher IV 42, and the valve port pressure difference of the variable-amplitude reversing valve 41 is controlled through the pressure matcher IV 42 so as to realize the proportional control of the variable-amplitude reversing valve 41.
Flexible switching-over antithetical couplet 2, hoist switching-over antithetical couplet 3 and change width of cloth switching-over antithetical couplet 4 in the present case belong to prior art respectively, specifically as follows:
as shown in fig. 1, a first working oil port of the three-way flow valve i 11, a first working oil port of the telescopic reversing valve 21, a first working oil port of the hoisting reversing valve 31, a first working oil port of the variable amplitude reversing valve 41, two working oil ports of the hydraulic control reversing valve 51, a first working oil port of the rotary reversing valve 61, two working oil ports of the check valve 71 and a first working oil port of the three-way flow valve seven 74 are all communicated with an oil inlet P1 of the first pump inlet control unit 1 and an oil inlet P2 of the second pump inlet control unit 7;
a second working oil port of the three-way flow valve I11, a first oil port of the load-sensitive LS oil path pressure-limiting overflow valve 14, a second working oil port of the telescopic reversing valve 21, a second working oil port of the winch reversing valve 31, a second working oil port of the variable amplitude reversing valve 41, a second working oil port of the rotary reversing valve 61 and another working oil port of the three-way flow valve seven 74 are all communicated with an oil return port T1 and an oil return port T2;
the control port of the three-way flow valve I11, the control oil port and the working oil port I of the pressure matcher II 22, the control oil port and the working oil port I of the pressure matcher III 32 and the control oil port and the working oil port I of the pressure matcher IV 42 are communicated with the control oil port of the pressure switching valve 72 sequentially through the hydraulic control reversing valve 51, the control oil port and the working oil port I of the pressure matcher VI 62 and are communicated with the control oil port of the three-way flow valve VII 74 through the pressure switching valve 72, and communication between the oil ports MLS1 and MLS2 is achieved;
the other two working oil ports of the telescopic reversing valve 21 are communicated with the two working oil ports of the second pressure matcher 22 and the other control port, the other two working oil ports of the winch reversing valve 31 are communicated with the two working oil ports of the third pressure matcher 32 and the other control port, the other two working oil ports of the variable amplitude reversing valve 41 are communicated with the two working oil ports of the fourth pressure matcher 42 and the other control port, and the other two working oil ports of the rotary reversing valve 61 are communicated with the two working oil ports of the sixth pressure matcher 62 and the other control port;
the oil port a in the rotary reversing link 6 is communicated with a control oil port of a hydraulic control reversing valve 51, and a spring cavity of the hydraulic control reversing valve 51 is communicated with oil return ports T1 and T2 through a damping five 52.
Further optimization, working oil ports of the telescopic reversing link 2, the winch reversing link 3, the variable amplitude reversing link 4 and the rotary reversing link 6 (working oil ports of the telescopic reversing valve 21, the winch reversing valve 31, the variable amplitude reversing valve 41, the confluence hydraulic control reversing valve 51 and the rotary reversing valve 61, such as working oil ports of A1, B1, A2, B2, A3, B3, A4 and B4 (A1-A4 and B1-B4 in the figure are corresponding reversing link working oil ports) can be combined and selectively provided with a plurality of pressure limiting overflow valves (23, 24, 33, 34, 43, 44, 63 and 64 in the figure 1), oil inlets of the pressure limiting overflow valves of the reversing valves are communicated with the corresponding working oil ports of the reversing valves, and oil return ports of the pressure limiting overflow valves are communicated with an oil return port T1 and an oil return port T2.
As shown in fig. 1, the specific working method is as follows:
when the crane system is in an unloaded state: any reversing link (a telescopic reversing link 2, a winch reversing link 3, a variable amplitude reversing link 4 and a rotary reversing link 6) of the proportional multi-way valve does not work, a hydraulic control reversing valve 51 of a main oil way in a confluence control link 5 is conducted due to a normally open function, hydraulic oil of a first oil pump is converged with an oil supply port P2 of a second oil pump through a first oil supply port P1, a load sensitive oil way LS1 of the first oil pump system and a load sensitive oil way LS2 of the second oil pump system are also connected in the multi-way valve, the oil way of the load sensitive oil way LS (LS is the name of the same oil way formed by the communication of the LS1 and the LS2 pipelines) has no feedback pressure, and a three-way flow valve I11 and a one-way valve 71 are opened and unloaded, so that the hydraulic oil of the two oil pumps flows out of the multi-way valve through an oil return port T1 and T2 and flows back to the oil tank, and the system only keeps very low standby pressure.
As shown in fig. 1, when the rotary reversing link 6 works and at least one of the telescopic reversing link 2, the winch reversing link 3 and the variable amplitude reversing link 4 works: the pressure of the oil port A4 and the oil port B4 of the rotary reversing linkage 6 enters the oil ports on the two sides of the shuttle valve 53 through control oil paths, and the shuttle valve 53 selects the oil path with high pressure in the oil port A4 and the oil port B4 and is communicated with the control oil port of the hydraulic control reversing valve 51 through the middle oil port of the shuttle valve 53. As long as the rotary reversing link 6 works, a pressure signal with high pressure in the oil ports A4 and B4 enters a control cavity of the hydraulic control reversing valve 51 through the shuttle valve 53 to push the hydraulic control reversing valve 51 to reverse and cut off a main oil path of the first oil pump and the second oil pump and a communicated oil path of a load sensitive LS oil path of each system of the first oil pump and the second oil pump, so that each system of the first oil pump and the second oil pump is separated, an oil supply port P2 of the second oil pump supplies oil and is independently used for the rotary reversing link 6 to perform the rotary operation of the crane, and an oil supply port P1 of the first oil pump supplies oil and is independently used for the working link operation in the telescopic reversing link 2, the winch reversing link 3 and the amplitude-variable reversing link 4.
The oil inlet control of the first oil pump is connected with 1, the pressure limiting of a main oil path is realized by adopting a load sensitive LS oil path pressure limiting overflow valve 14 to pilot control a three-way flow valve I11, and the pressure limiting of the main oil path is generally set to be high (for example, an oil supply port P1 = 30MPa of the first oil pump) so as to meet the requirement of high load pressure of a telescopic reversing connection 2, a winch reversing connection 3 and a variable amplitude reversing connection 4; a load sensitive LS2 oil path from the rotary reversing linkage 6, a pressure switching valve 72 with a normally open function is connected with a control port of a three-way flow valve seven 74, a control cavity of the pressure switching valve 72 is also directly connected with a load sensitive LS2 oil path from the rotary reversing linkage 6, and the set pressure value of the pressure switching valve 72 is generally lower (for example, a second oil pump oil supply port P2 = 16 MPa); when the pressure of the oil line of the load-sensitive LS2 from the rotary reversing link 6 is not higher than a set value, the pressure switching valve 72 directly acts on a control port of the three-way flow valve seven 74, and at the moment, the three-way flow valve seven 74 enables the second pump system to generate working pressure corresponding to the load-sensitive LS 2; when the pressure of a load sensitive LS2 oil line from the rotary reversing joint 6 is higher than the set value of the pressure switching valve 72, the pressure switching valve 72 is closed, the control cavity of the three-way flow valve seven 74 is opened through the pressure relief of the damping seven 73, and the P2 pump port of the second pump system can realize low-pressure unloading.
The working pressure of the rotary reversing coupling 6 is generally set to be low (for example, the oil supply port P2 = 16MPa of the second oil pump), and the actual working pressure requirement of the rotary reversing coupling 6 can be met. When the rotary union works, the hydraulic control reversing valve 51 of the confluence control valve 5 reverses, the communication between the first oil pump oil supply port P1 and the second oil pump oil supply port P2 is cut off, the load-sensitive LS1 oil path and the load-sensitive LS2 oil path is cut off, and the load pressure of the rotary union 6 is fed back by the load-sensitive LS2 oil path; when the rotary reversing connection 6 does not work and the hydraulic control reversing valve 51 does not reverse, the feedback is the load pressure of other connections except the rotary reversing connection 6, the three-way flow valve seven 74 is also controlled by the pilot pressure limiting of the load-sensitive LS1 oil path pilot overflow valve 14 on the first oil pump oil inlet control connection 1 in the multi-way valve confluence state, namely the pressure limiting set pressure of the three-way flow valve seven 74 is the same as the pressure limiting set pressure of the three-way flow valve one 11. When the rotary reversing joint 6 does not work and the multi-way valve is in a confluence state, the pressures of the first oil pump port P1 and the second oil pump port P2 rise along with the increase of the load, when the load pressure rises to a set pressure (such as 16 MPa) value of the pressure switching valve 72 of the oil inlet control joint 7, the pressure switching valve 72 is closed, the second oil pump oil supply port P2 is unloaded at low pressure under the action of the three-way flow valve seven 74, and at the moment, the one-way valve 71 is stopped, so that the first oil pump system continues to normally work without being influenced by the unloading of the second oil pump system. The pressure of the second oil pump independent supply rotary reversing coupling 6 is very low, so that the torque taken by the second oil pump independent supply rotary reversing coupling to the chassis engine can not rise along with the lifting of the working load of the first oil pump system any more, and the effect is that when the first oil pump system works under a high load, the total output torque demand of the engine is restrained, so that the phenomenon that the engine is suppressed and stalled is avoided.
The disclosure of the present application also includes the following points:
(1) the drawings of the embodiments disclosed herein only relate to the structures related to the embodiments disclosed herein, and other structures can refer to general designs;
(2) in case of conflict, the embodiments and features of the embodiments disclosed in this application can be combined with each other to arrive at new embodiments;
the above embodiments are only embodiments disclosed in the present disclosure, but the scope of the disclosure is not limited thereto, and the scope of the disclosure should be determined by the scope of the claims.
Claims (10)
1. The double fixed displacement pump confluence multiway valve is characterized by comprising a first pump oil inlet control union (1), a proportional reversing valve working union, a confluence control union (5), a rotary reversing union (6) and a second pump oil inlet control union (7);
the first pump oil inlet control unit (1) supplies oil to the proportional directional valve working unit through a first quantitative oil pump;
the second pump oil inlet control joint (7) supplies oil to the rotary reversing joint (6) through a second quantitative oil pump;
the confluence control joint (5) is arranged between the first pump oil inlet control joint (1) and the second pump oil inlet control joint (7) and controls the confluence of the first quantitative oil pump and the second quantitative oil pump;
the confluence control union (5) comprises a hydraulic control reversing valve (51) and a shuttle valve (53);
the rotary reversing joint (6) controls the connection and disconnection of a confluence channel of a first quantitative oil pump and a second quantitative oil pump through the hydraulic control reversing valve (51), so that the second quantitative oil pump independently supplies oil to the rotary reversing joint (6) when the rotary reversing joint (6) is in a working state;
an A4 oil port and a B4 oil port of the rotary reversing link (6) are respectively connected with working oil ports on two sides of the shuttle valve (53);
and a middle working oil port of the shuttle valve (53) is communicated with a control oil port of the hydraulic control reversing valve (51).
2. The double fixed displacement pump converging multi-way valve of claim 1 wherein the converging control manifold (5) further comprises a damping five (52);
and the damping five (52) is arranged on a spring cavity oil return circuit of the hydraulic control reversing valve (51) and is used for controlling the reversing action speed of a valve core of the hydraulic control reversing valve (51).
3. The double fixed displacement pump converging multi-way valve as defined in claim 1, wherein the rotary reversing union (6) comprises a rotary reversing valve (61) and a pressure adapter six (62);
a first working oil port of the rotary reversing valve (61) is communicated with an oil inlet P1 and an oil inlet P2;
a second working oil port of the rotary reversing valve (61) is communicated with an oil return port T1 and an oil return port T2;
the other two working oil ports of the rotary reversing valve (61) are communicated with a pressure matcher six (62);
two working oil ports of the hydraulic control reversing valve (51) are communicated with a first control oil port and a first working oil port of a pressure matcher six (62), and the communication of the oil ports MLS1 and MLS2 is realized through the second pump oil inlet control union (7).
4. The double fixed displacement pump converging multi-way valve as claimed in claim 3, wherein the rotary reversing union (6) further comprises a first pressure limiting overflow valve six (63) and a second pressure limiting overflow valve six (64);
one end of the first pressure limiting overflow valve six (63) is communicated with an oil return port T2, and the other end of the first pressure limiting overflow valve six (63) is communicated with an A4 working oil port;
one end of the second pressure limiting overflow valve six (64) is communicated with the oil return port T2, and the other end of the second pressure limiting overflow valve six (64) is communicated with the B4 working oil port.
5. The double fixed displacement pump confluence multiport valve as claimed in claim 3, wherein said second pump inlet oil control manifold (7) comprises a one-way valve (71), a pressure switching valve (72), a damping seven (73) and a three-way flow valve seven (74);
the oil inlet P2 supplies oil to the rotary reversing joint (6) through the one-way valve (71) and is communicated with an oil inlet of the three-way flow valve seven (74);
an oil outlet of the three-way flow valve seven (74) and the damping seven (73) are respectively communicated with an oil return port T2;
and the load sensitive oil path LS2 is communicated with a spring cavity of the three-way flow valve seven (74) and a working oil port of the damping seven (73) through the pressure switching valve (72).
6. The double fixed displacement pump confluence multi-way valve as claimed in claim 1, wherein the first pump inlet control union (1) comprises a three-way flow valve I (11), a damping I (13) and a load sensitive LS oil path pressure limiting overflow valve (14);
the LS1 control oil way is communicated with the oil return port T1 through a first damper (13);
a first working oil port of the three-way flow valve I (11) is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
an oil port I of the load-sensitive LS oil path pressure-limiting overflow valve (14) is communicated with an oil return port T1, and an oil port II of the load-sensitive LS oil path pressure-limiting overflow valve is communicated with a load-sensitive oil path pressure measuring oil port MLS 1;
and a control oil port of the three-way flow valve I (11) is connected to a connection oil path between the load-sensitive LS oil path pressure-limiting overflow valve (14) and a load-sensitive oil path pressure-measuring oil port MLS 1.
7. The double fixed displacement pump confluence multi-way valve as claimed in claim 1, wherein the proportional reversing valve working unit comprises one or a combination of any more of a telescopic reversing unit (2), a winch reversing unit (3) and a variable amplitude reversing unit (4).
8. The double fixed displacement pump converging multi-way valve as claimed in claim 7, wherein the telescopic reversing union (2) comprises a telescopic reversing valve (21) and a second pressure matcher (22);
a first working oil port of the telescopic reversing valve (21) is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the second pressure matcher (22) is communicated with a first working oil port and the second pump oil inlet control connector (7);
the telescopic reversing valve (21) is communicated with a second pressure matcher (22), and the valve port pressure difference of the telescopic reversing valve (21) is controlled through the second pressure matcher (22) so as to realize the proportional control of the telescopic reversing valve (21).
9. The double fixed displacement pump converging multi-way valve as claimed in claim 7, wherein the hoisting reversing union (3) comprises a hoisting reversing valve (31) and a pressure matcher III (32);
a first working oil port of the winch reversing valve (31) is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the third pressure matcher (32) is communicated with a first working oil port and the second pump oil inlet control connector (7);
the winch reversing valve (31) is communicated with a third pressure matcher (32), and the valve port pressure difference of the winch reversing valve (31) is controlled through the third pressure matcher (32) so as to realize the proportional control of the winch reversing valve (31).
10. The double fixed displacement pump confluence multiport valve as claimed in claim 7, wherein said variable amplitude reversing union (4) comprises a variable amplitude reversing valve (41) and a pressure matcher four (42);
a first working oil port of the variable amplitude reversing valve (41) is communicated with an oil inlet P1, and a second working oil port is communicated with an oil return port T1;
a control oil port of the pressure matcher IV (42) is communicated with a working oil port I and the second pump oil inlet control connector (7);
the variable-amplitude reversing valve (41) is communicated with a pressure matcher IV (42), and the valve port pressure difference of the variable-amplitude reversing valve (41) is controlled through the pressure matcher IV (42) so as to realize the proportional control of the variable-amplitude reversing valve (41).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122325379.1U CN216190493U (en) | 2021-09-24 | 2021-09-24 | Double-fixed displacement pump converging multi-way valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122325379.1U CN216190493U (en) | 2021-09-24 | 2021-09-24 | Double-fixed displacement pump converging multi-way valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN216190493U true CN216190493U (en) | 2022-04-05 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122325379.1U Active CN216190493U (en) | 2021-09-24 | 2021-09-24 | Double-fixed displacement pump converging multi-way valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN216190493U (en) |
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2021
- 2021-09-24 CN CN202122325379.1U patent/CN216190493U/en active Active
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