WO2025007488A1 - 多路换向阀、支腿油缸控制系统和汽车起重机 - Google Patents

多路换向阀、支腿油缸控制系统和汽车起重机 Download PDF

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Publication number
WO2025007488A1
WO2025007488A1 PCT/CN2023/136157 CN2023136157W WO2025007488A1 WO 2025007488 A1 WO2025007488 A1 WO 2025007488A1 CN 2023136157 W CN2023136157 W CN 2023136157W WO 2025007488 A1 WO2025007488 A1 WO 2025007488A1
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WIPO (PCT)
Prior art keywords
valve
oil
cylinder
port
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2023/136157
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English (en)
French (fr)
Inventor
廖启辉
何伟
沈昌武
周庆喜
窦发磊
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Zoomlion Heavy Industry Science and Technology Co Ltd
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Zoomlion Heavy Industry Science and Technology Co Ltd
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Publication of WO2025007488A1 publication Critical patent/WO2025007488A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • B66C13/20—Control systems or devices for non-electric drives
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
    • B66C23/18—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes
    • B66C23/36—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes specially adapted for use in particular purposes mounted on road or rail vehicles; Manually-movable jib-cranes for use in workshops; Floating cranes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/027—Check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/007—Overload

Definitions

  • the present application belongs to the field of outrigger systems of engineering machinery, and in particular, relates to an automobile crane, an outrigger oil cylinder control system and a multi-way reversing valve used therein.
  • the outrigger system generally includes a horizontal cylinder that extends horizontally and a vertical cylinder that extends vertically.
  • the vertical cylinder has higher requirements for its model selection and telescopic stability during use.
  • the vertical cylinder and the horizontal cylinder should be able to be controlled completely independently without affecting each other. In this way, not only can cylinders of different sizes and functions be controlled independently, but it is also safer and more reliable. More importantly, from the user's perspective, if the horizontal cylinder also produces additional linkage action when the button for controlling the vertical cylinder alone is pressed, the user's perception will be poor, and the reliability of the outrigger control will be doubted. If the horizontal cylinder retracts when the vertical cylinder is under force, it is also easy to damage the stability of the vertical cylinder.
  • the purpose of the present application is to provide a multi-way reversing valve, an outrigger cylinder control system and a truck crane to improve the control independence, reliability and user satisfaction of the outrigger system.
  • a multi-way reversing valve comprising:
  • the telescopic function selection valve includes a main oil inlet and a main oil return port on one side and a rod chamber connecting oil port and a rodless chamber connecting oil port on the other side;
  • a plurality of oil cylinder type selection valves wherein the oil inlet on one side of each of the oil cylinder type selection valves is connected in parallel to the rodless chamber oil inlet and return path connected to the rodless chamber connecting oil port, and the working oil port on the other side of the oil cylinder type selection valve is used to connect to the rodless chamber;
  • an externally controlled overload valve connected to the working oil port of the oil cylinder type selection valve and used for maintaining pressure or unloading the working oil port, a first end pilot control oil circuit is connected between the first control end of the externally controlled overload valve and the rod chamber connecting oil port, and a second control end of the externally controlled overload valve is connected to the working oil port of the oil cylinder type selection valve;
  • a control valve is arranged in the first end pilot control oil circuit.
  • control valve is a hydraulically controlled one-way valve and is configured to allow hydraulic oil to flow from the rod chamber connecting oil port to the first control end and be blocked in the reverse direction.
  • the hydraulic control end of the hydraulically controlled one-way valve is connected to the rodless chamber inlet and return oil circuit for reverse opening of the one-way valve.
  • the control valve is a hydraulically controlled reversing valve and includes a first reversing valve position and a second reversing valve position.
  • the first reversing valve position is provided with a one-way stop valve, and the one-way stop valve is configured to allow hydraulic oil to flow from the rod chamber connecting oil port to the first control end and to stop in the opposite direction.
  • the second reversing valve position is an oil circuit conduction position, and the hydraulic control end of the hydraulically controlled reversing valve is connected to the rodless chamber inlet and return oil circuit for switching to the second reversing valve position.
  • the multi-way reversing valve comprises:
  • a rod chamber oil inlet and return passage connected to the rod chamber oil connection port and used to connect to the rod chamber of each oil cylinder;
  • a main one-way valve is arranged in the oil inlet and return path of the rod chamber and is arranged to allow hydraulic oil to flow from the rod chamber connecting oil port to the rod chamber and to cut off the reverse direction;
  • the main check valve is connected to the rodless chamber inlet and return oil circuit through a pilot oil circuit for Open the main check valve in reverse.
  • the first control end of the externally controlled overload valve is a spring control end provided with a compression spring.
  • the multi-way reversing valve comprises:
  • a main overflow valve arranged between the main oil inlet and the main oil return port;
  • the set spring pressure of the compression spring at the first control end of the externally controlled overload valve is smaller than the set overflow pressure of the main overflow valve.
  • the working oil port of the cylinder type selection valve includes a first working oil port connected to the rodless chamber of the vertical cylinder and a second working oil port connected to the rodless chamber of the horizontal cylinder.
  • the cylinder type selection valve is used to selectively switch the oil inlet on one side to the first working oil port or the second working oil port on the other side, and the externally controlled overload valve is connected to the first working oil port or the second working oil port.
  • the plurality of cylinder type selection valves include:
  • a double-cylinder type selection valve wherein the first working oil port of the double-cylinder type selection valve is connected to the rodless chamber of the vertical cylinder, and the second working oil port is connected to the rodless chamber of the horizontal cylinder;
  • a single cylinder type selection valve wherein the first working oil port of the single cylinder type selection valve is connected to the rodless chamber of the vertical cylinder, and the second working oil port is cut off;
  • the second control end of the externally controlled overload valve is connected to the second working oil port of the dual-cylinder type selection valve, and the second control end of the externally controlled overload valve is connected to the first working oil port of the single-cylinder type selection valve.
  • a one-way pressure-maintaining valve is provided in the connecting oil circuit connecting the externally controlled overload valve and the first working oil port or the second working oil port of the cylinder type selection valve, and the one-way pressure-maintaining valve is configured to allow hydraulic oil to flow from the cylinder type selection valve to the externally controlled overload valve and to be blocked in the reverse direction.
  • an outrigger oil cylinder control system comprising an outrigger oil cylinder
  • the cylinder group and the above-mentioned multi-way reversing valve, the multi-way reversing valve is used for hydraulically controlling the outrigger oil cylinder group.
  • the outrigger cylinder group includes four groups of lateral outrigger cylinder groups and four cylinder type selection valves that control the four groups of lateral outrigger cylinder groups one by one, each group of lateral outrigger cylinder groups includes a vertical cylinder and a horizontal cylinder, and each of the cylinder type selection valves is used to switch the rodless cavity inlet and return oil circuits to the rodless cavity of the vertical cylinder or the rodless cavity of the horizontal cylinder in the corresponding lateral outrigger cylinder group.
  • a bidirectional hydraulic lock is provided in the working oil circuit of the vertical cylinder.
  • a truck crane is provided, and the truck crane comprises the above-mentioned outrigger cylinder control system.
  • a control valve is added to the first end pilot control oil circuit of the external control overload valve to realize the pressure maintaining function or unloading function of the external control overload valve in a switch control manner.
  • the control valve has a one-way cut-off function.
  • FIG1 is a hydraulic structure diagram of a multi-way reversing valve according to a specific embodiment of the present application.
  • FIG2 is a hydraulic principle diagram of an outrigger oil cylinder control system according to a first embodiment of the present application, in which the multi-way reversing valve shown in FIG1 is used and each link is in a neutral position;
  • FIG3 is a hydraulic principle diagram of the outrigger cylinder control system shown in FIG2 when performing a retracting vertical cylinder action;
  • FIG4 is a hydraulic principle diagram of the outrigger cylinder control system shown in FIG2 when executing the horizontal cylinder extension action;
  • FIG5 is a hydraulic structure diagram of a two-position, two-way hydraulically controlled directional valve.
  • FIG6 is a hydraulic principle diagram of an outrigger cylinder control system according to a second embodiment of the present application.
  • Multi-way reversing valves are widely used in engineering machinery.
  • the multi-way reversing valve and outrigger cylinder control system in the following implementation is mainly used to control the horizontal outrigger cylinder (referred to as horizontal cylinder) and vertical outrigger cylinder (referred to as vertical cylinder) of a truck crane.
  • the multi-way reversing valve comprises:
  • the telescopic function selection valve 1.1 comprises a main oil inlet port P and a main oil return port T on one side and a rod chamber connecting oil port c and a rodless chamber connecting oil port e on the other side;
  • a plurality of oil cylinder type selection valves the oil inlet on one side of each oil cylinder type selection valve is connected in parallel to the rodless chamber inlet and return oil path L1 connected to the rodless chamber connecting oil port e, and the working oil port on the other side of the oil cylinder type selection valve is used to connect to the rodless chamber;
  • An externally controlled overload valve 7 is connected to the working oil port of the cylinder type selection valve and is used for maintaining pressure or unloading the working oil port.
  • a first end pilot control oil circuit is connected between the first control end of the externally controlled overload valve 7 and the rod chamber connecting oil port c.
  • the second control end of the externally controlled overload valve 7 is connected to the working oil port of the cylinder type selection valve;
  • the control valve 9 is arranged in the first end pilot control oil circuit.
  • the multi-way reversing valve of this embodiment can be used to control the outrigger system of a truck crane, as shown in FIG3 , and is applied to the outrigger cylinder control system.
  • the telescopic function selection valve 1.1 selects the extension or retraction function, that is, the upper valve position of the telescopic function selection valve 1.1 shown in FIG1 is used to control the outrigger cylinder to perform the extension action, and the lower valve position is used to control the outrigger cylinder to perform the retraction action.
  • the cylinder type selection valves 1.2-1.6 are used to select the corresponding vertical cylinder or horizontal cylinder to perform the extension or retraction function selected by the telescopic function selection valve 1.1.
  • the pressure oil enters the telescopic function selection valve 1.1 from the main oil inlet P.
  • the telescopic function selection valve 1.1 has three oil ports a1, a2 and f on the left side, and three working oil ports b, c and f on the right side. That is, the telescopic function selection valve 1.1 shown in FIG. 1 is a three-position six-way reversing valve, but this is only an example.
  • the telescopic function selection valve 1.1 of the present application is not limited to this, and may also be other multi-position multi-way reversing valves.
  • the rod chamber connecting oil port c on the right side of the telescopic function selection valve 1.1 is connected to the rod chamber inlet and return oil port.
  • Road L0, and the rodless chamber connecting oil port e is connected to the rodless chamber inlet and return oil circuit L1
  • the oil inlets of multiple cylinder type selection valves 1.2-1.6 are connected in parallel to the rodless chamber inlet and return oil circuit L1
  • the hydraulic oil in the rodless chamber inlet and return oil circuit L1 is connected to the rodless chamber of the corresponding horizontal cylinder or vertical cylinder through the valve position switching of the cylinder type selection valve.
  • one of the working oil ports of the oil cylinder type selection valve is connected to an externally controlled overload valve 7, which is used to unload when the oil pressure in the rodless chamber of the oil cylinder is too high.
  • the externally controlled overload valve 7 generally adopts a hydraulic control method, as shown in Figure 1, the first control end of the externally controlled overload valve 7 is connected to the rod chamber connecting oil port c, and the second control end of the externally controlled overload valve 7 is connected to the working oil port of the oil cylinder type selection valve.
  • the multi-way reversing valve includes basic valve components such as the telescopic function selection valve 1.1, multiple cylinder type selection valves 1.2-1.6 and an externally controlled overload valve 7.
  • the vertical cylinders 4.1-4.5 including four vertical cylinders on the left and right sides and the fifth vertical cylinder under the cab
  • the horizontal cylinders 5.1-5.4 including four horizontal cylinders on the left and right sides
  • the telescopic function selection valve 1.1 is switched to the upper valve position corresponding to the extension action, and the cylinder type selection valves 1.3-1.6 are switched to the lower valve position corresponding to the horizontal cylinder.
  • the pressure oil enters the a1 and a2 oil ports on the left side of the telescopic function selection valve 1.1 from the P port.
  • the a2 port is connected to the e port, and the pressure oil reaches the rodless chamber return oil circuit L1, and then reaches the oil inlet s2-s5 of the cylinder type selection valve 1.3-1.6.
  • the internal oil passages of s1-v1, s2-v2, s3-v3, s4-v4, and s5-v5 in the cylinder type selection valve 1.3-1.6 are connected, and then flow into the rodless chamber of the corresponding horizontal cylinder 5.1-5.4 through the respective horizontal cylinder rod chamber oil circuit L3.
  • the pressure oil flows into the inlet w of the external control overload valve 7.
  • the external control overload valve 7 opens to play an overload protection role.
  • the oil in the rod chamber of the horizontal cylinder 5.1-5.4 returns to the right side C port of the telescopic function selection valve 1.1 through the rod chamber return oil path L0, and the flow channel cf is connected, and finally flows back to the T port.
  • the pressure oil enters the left oil ports a1 and a2 of the telescopic function selection valve 1.1 from the P port, and the telescopic function selection valve 1.1 switches to the lower valve position corresponding to the retraction function.
  • a2 is connected to c
  • e is connected to f.
  • the pressure oil passes through the a2 port of the telescopic function selection valve 1.1 to the c port, and the oil flows into the rod chamber of the horizontal oil cylinder 5.1-5.4 through the rod chamber return oil path L0.
  • the telescopic function selection valve 1.1 When the vertical oil cylinders 4.1-4.5 are retracted to their full position, the telescopic function selection valve 1.1 returns to the middle position. At this time, c, e and f are connected, c and e are connected to unload, and the oil in the rod chamber of the horizontal oil cylinder 5.1-5.4 is locked in the pipeline by the one-way cut-off function of the main one-way valve 2 in the rod chamber inlet and return oil circuit L0, and cannot be released, and each rod chamber maintains high pressure.
  • the control chamber e-n previously loaded to the external control overload valve 7 is unloaded due to the telescopic function selection valve 1.1 returning to the middle position, so that the pressure of the inlet w and d1, d2, d3, d4, d5 of the external control overload valve 7 can only be maintained at its set pressure.
  • the oil pressure of the rod chamber is greater than the oil pressure of the rodless chamber, and the oil in the rodless chamber flows from v2-d2-w, v3-d3-w, v4-d4-w, v5-d5-w through the external control overload valve 7 to the T port, resulting in the retraction of the horizontal oil cylinder 5.1-5.4.
  • the present application adds a control valve 9 in the first end pilot control oil circuit to switch
  • the control method realizes the pressure-maintaining function or unloading function of the external control overload valve 7. Because the control valve 9 has a one-way cut-off function, when the rod chamber inlet and return oil circuit L0 loses pressure, the pressure of the first end pilot control oil circuit of the external control overload valve 7 will be maintained, and the external control overload valve 7 will remain in a closed state, thereby ensuring that the horizontal cylinders 5.1-5.4 remain in their original positions. In this way, the phenomenon of synchronous retraction of the horizontal cylinder can be well solved after the vertical cylinder retracts to the full position and the telescopic function selection valve returns to the middle position.
  • control valve 9 adopts a hydraulically controlled one-way valve and is configured to enable hydraulic oil to flow from the rod chamber connecting oil port c to the first control end and be blocked in the reverse direction.
  • the hydraulic control end of the hydraulically controlled one-way valve is connected to the rodless chamber inlet and return oil circuit L1 for reverse opening of the one-way valve.
  • the control valve 9 adopts a hydraulically controlled reversing valve and includes a first reversing valve position (the left valve position shown in FIG. 5) and a second reversing valve position (the right valve position shown in FIG. 5).
  • a one-way stop valve is provided in the internal oil passage km of the first reversing valve position.
  • the one-way stop valve is set to allow hydraulic oil to flow from the rod chamber connecting oil port c to the first control end and to be blocked in the reverse direction.
  • the second reversing valve position is an oil circuit conduction position, that is, the internal oil passage km is always unobstructed at the second reversing valve position.
  • the hydraulic control end l of the hydraulically controlled reversing valve is connected to the rodless chamber inlet and return oil circuit L1 (i.e., port e).
  • L1 i.e., port e
  • the valve core of the hydraulically controlled reversing valve can be switched to the second reversing valve position.
  • a hydraulically controlled one-way valve or a hydraulically controlled reversing valve, or even other valve forms is used, by adding a hydraulically controlled one-way valve with a reverse cut-off function or a two-position two-way reversing valve with a one-way cut-off function between the right side port c of the telescopic function selection valve 1.1 and the first control end of the external control overload valve 7, the pressure locking function of the control chamber of the external control overload valve 7 can be realized, and the control chamber can be unloaded when it is released.
  • the multi-way reversing valve includes a main overflow valve 6, which is arranged between the main oil inlet P and the main oil return port T.
  • the first control end of the external overload valve 7 is a spring control end provided with a compression spring.
  • the external overload valve 7 is used to protect the horizontal cylinder and the vertical cylinder 4.5 from overload.
  • the set spring pressure of the compression spring at the first control end of the external overload valve 7 is less than the set relief pressure of the main relief valve 6.
  • the set spring pressure of the external overload valve 7 is 7MPa
  • the set relief pressure of the main relief valve 6 is 20MPa.
  • the multi-way reversing valve comprises:
  • the rod chamber inlet and return oil passage L0 is connected to the rod chamber connecting oil port c and is used to connect to the rod chamber of each cylinder;
  • a main check valve 2 is arranged in the rod chamber inlet and return oil path L0 and is arranged to allow the hydraulic oil to flow from the rod chamber connecting oil port c to the rod chamber and to cut off the reverse direction;
  • the main check valve 2 is connected to the rodless chamber inlet and return oil circuit L1 through a pilot oil circuit so as to open the main check valve 2 in reverse.
  • the setting of the main check valve 2 can ensure that the pressure of the rod chamber of the oil cylinder is maintained when needed, or it can be opened in the reverse direction when needed, thereby ensuring that the oil return path L0 of the rod chamber is unobstructed and ensuring smooth unloading of the rod chamber.
  • the working oil port of the cylinder type selection valve includes a first working oil port (for example, t2 oil port) connected to the rodless chamber of the vertical cylinder and a second working oil port (for example, v2 oil port) connected to the rodless chamber of the horizontal cylinder.
  • the cylinder type selection valve is used to selectively switch the oil inlet on one side to the first working oil port or the second working oil port on the other side, and the externally controlled overload valve 7 is connected to the first working oil port or the second working oil port.
  • a double cylinder type selection valve wherein a first working oil port of the double cylinder type selection valve is connected to a rodless chamber of a vertical cylinder, and a second working oil port is connected to a rodless chamber of a horizontal cylinder;
  • a single cylinder type selection valve wherein the first working oil port of the single cylinder type selection valve is connected to the rodless chamber of the vertical cylinder, and the second working oil port is cut off;
  • the second control end of the external overload valve 7 is connected to the second working oil port of the double-cylinder type selection valve, and the second control end of the external overload valve 7 is connected to the first working oil port of the single-cylinder type selection valve. Oil port connected.
  • the outrigger cylinder control system when applied to the outrigger cylinder control system shown in FIG. 2 to FIG. 4 and FIG. 6 , the outrigger cylinder control system includes an outrigger cylinder group and the above-mentioned multi-way reversing valve, and the multi-way reversing valve is used to hydraulically control the outrigger cylinder group.
  • the cylinder type selection valves 1.3-1.6 are double cylinder type selection valves for controlling the four groups of side outrigger cylinder groups, and the cylinder type selection valve 1.2 is a single cylinder type selection valve for controlling the fifth vertical cylinder.
  • the double cylinder type selection valve is switched between the upper and lower valve positions, the rodless chamber inlet and return oil circuit L1 can be switched to connect to the vertical cylinder rod chamber oil circuit L2 or the horizontal cylinder rod chamber oil circuit L3.
  • the outrigger cylinder group illustrated in this article includes four groups of side outrigger cylinder groups and four cylinder type selection valves that control the four groups of side outrigger cylinder groups one by one, each group of side outrigger cylinder groups includes a vertical cylinder and a horizontal cylinder, and each cylinder type selection valve is used to switch the rodless chamber inlet and return oil circuit to the rodless chamber of the vertical cylinder or the rodless chamber of the horizontal cylinder in the corresponding side outrigger cylinder group.
  • the single cylinder type selection valve shown in the figure i.e., the cylinder type selection valve 1.2, has only the upper valve position as the connection position, and the middle position and the lower position are both cut-off positions, i.e., it is used to control the vertical cylinder 4.5 only when it is switched to the upper valve position.
  • a two-way hydraulic lock 3.1-3.5 is provided in the working oil circuit of the vertical cylinder for maintaining the pressure of the cylinder.
  • a one-way pressure-maintaining valve 8.1-8.5 is provided in the connecting oil circuit connecting the externally controlled overload valve 7 and the first working oil port or the second working oil port of the cylinder type selection valve to prevent the horizontal cylinders from affecting each other.
  • the one-way pressure-maintaining valve 8.1-8.5 is configured to allow the hydraulic oil to flow from the cylinder type selection valve 1.2-1.6 to the externally controlled overload valve 7 and be blocked in the reverse direction.
  • the multi-way reversing valve and outrigger oil cylinder control system of the present application has the advantages of simple structure, safety and reliability, etc.
  • the telescopic control of the nine outrigger oil cylinders is realized, and at the same time, it has safety protection function and overload protection.
  • the main check valve 2 can effectively prevent the horizontal oil cylinder from being thrown out during the driving process of the truck crane.
  • the combined oil circuit of the external control overload valve 7 and its control valve 9 can prevent the horizontal oil cylinder from automatically retracting due to pressure difference after the vertical oil cylinder is retracted and the telescopic function selection valve stem returns to the middle position.
  • the rodless chamber of the vertical cylinder 4.1-4.5 is connected to t1-t5 corresponding to the cylinder type selection valve 1.2-1.6, and t1-s1-e-f-T, t2-s2-e-f-T, t3-s3-e-f-T, t4-s4-e-f-T, and t5-s5-e-f-T are connected, that is, the rodless chamber returns oil through the rodless chamber return oil circuit L1.
  • the reverse cut-off function of the hydraulic control one-way valve can be used to ensure that the first end control chamber n of the external control overload valve 7 always maintains the pressure set by the main relief valve 6. Therefore, even if the telescopic function selection valve 1.1 is switched to the middle position, the external control overload valve 7 It can still be closed effectively without overflow.
  • the oil in the rodless chamber of the horizontal cylinder 5.1-5.4 is kept between v2-d2-w, v3-d3-w, v4-d4-w, and v5-d5-w, and the oil in the rodless chamber of the vertical cylinder 4.5 is kept between r5-t1-d1-w, and the pressure remains basically unchanged.
  • the outrigger cylinder control system is in the process of executing the horizontal cylinder extension action.
  • the oil from port e opens the control valve 9 in reverse through the el pilot oil circuit, and opens the main check valve 2 in reverse through the ej pilot oil circuit; h-g is connected, and the rod chamber returns to the return oil circuit L0, and the oil in the rod chamber of the horizontal cylinder 5.1-5.4 flows back from the rodless chamber-h-g-c-f-T, that is, the horizontal cylinder 5.1-5.4 returns oil; n-m-k-c-f-T is connected, and the control chamber n of the externally controlled overload valve 7 is unloaded.
  • a two-position two-way reversing valve is used to replace the control valve 9 as the hydraulically controlled check valve in FIG2.
  • the oil at the P port passes through a2-cg through the main check valve 2, and then enters the h
  • the control oil flows from port c to port k through the one-way valve in the left position of the control valve 9 as a two-position two-way reversing valve, and reaches the control chamber n of the external control overload valve 7, ensuring that the control chamber n of the external control overload valve 7 maintains high pressure.
  • the pressure oil can switch the two-position two-way reversing valve to the right position through the el pilot oil circuit, and the oil in the control chamber of the external control overload valve 7 passes through the n-m-k-c oil circuit, the c-f channel of the telescopic function selection valve 1.1, and is unloaded through the T port.
  • the end pressure of the external control overload valve 7 is the set spring pressure, which can realize the overload protection of the horizontal oil cylinder 5.1-5.4.
  • the present application also protects a truck crane, including the above-mentioned outrigger oil cylinder control system.
  • the truck crane of the present application has better maneuverability, and its outrigger system does not explain the linkage status of the vertical oil cylinder and the horizontal oil cylinder, thereby improving product performance.
  • first and second are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as “first” or “second” may explicitly or implicitly include at least one of the features.
  • “plurality” means at least two, such as two, three, etc., unless otherwise clearly and specifically defined.
  • the terms “installed”, “connected”, “connected”, “fixed” and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection, an electrical connection, or communication with each other; it can be a direct connection, or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined.
  • installed installed”, “connected”, “connected”, “fixed” and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection, an electrical connection, or communication with each other; it can be a direct connection, or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined.
  • the specific meanings of the above terms in this application can be understood according to specific circumstances.

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Abstract

一种多路换向阀、支腿油缸控制系统和汽车起重机，多路换向阀包括伸缩功能选择阀，包括一侧的主进油口、主回油口和另一侧的有杆腔连接油口、无杆腔连接油口；若干油缸类型选择阀，各个油缸类型选择阀的一侧的进油口并联连接至与无杆腔连接油口相连的无杆腔进回油路，油缸类型选择阀的另一侧的工作油口用于连接至无杆腔；外控过载阀，与油缸类型选择阀的工作油口相连并用于工作油口的保压或卸荷，外控过载阀的第一控制端与有杆腔连接油口之间连接有第一端先导控制油路，外控过载阀的第二控制端与油缸类型选择阀的工作油口连接；和控制阀，设置在第一端先导控制油路中。可提升支腿系统的控制独立性、可靠性和用户满意度。

Description

多路换向阀、支腿油缸控制系统和汽车起重机
相关申请的交叉引用
本申请要求2023年7月4日提交的中国专利申请202310814982.7的权益，该申请的内容通过引用被合并于本文。
技术领域
本申请属于工程机械的支腿系统领域，具体地，涉及一种汽车起重机、支腿油缸控制系统及其使用的多路换向阀。
背景技术
随着汽车起重机的发展，起重臂越来越长，起吊顿重也越来越重，因此对机身的支腿系统的要求也越来越高。支腿系统一般包括侧向水平伸出的水平油缸和竖向伸出的垂直油缸，水平油缸的活塞杆伸缩行程越长，机身的支护稳定性更好，垂直油缸作为主要受力部件，其型号选择和使用过程的伸缩平稳性要求较高。
一般而言，在支腿系统的伸缩过程中，垂直油缸和水平油缸应能够完全独立控制，互不影响。如此不仅型号大小不同、功能不同的油缸能够独立受控，更安全可靠。更重要的是，站在使用者角度，若按下单独控制垂直油缸的按键时，水平油缸也产生额外的联动动作，则用户感受度较差，怀疑支腿控制的可靠性。若垂直油缸在受力时，水平油缸缩回，也容易对垂直油缸的稳定性产生破坏。
发明内容
本申请的目的是提供一种多路换向阀、支腿油缸控制系统和汽车起重机，以提升支腿系统的控制独立性、可靠性和用户满意度。
为了实现上述目的，根据本申请的第一方面，提供一种多路换向阀，包括：
伸缩功能选择阀，包括一侧的主进油口、主回油口和另一侧的有杆腔连接油口、无杆腔连接油口；
若干油缸类型选择阀，各个所述油缸类型选择阀的一侧的进油口并联连接至与所述无杆腔连接油口相连的无杆腔进回油路，所述油缸类型选择阀的另一侧的工作油口用于连接至无杆腔；
外控过载阀，与所述油缸类型选择阀的工作油口相连并用于所述工作油口的保压或卸荷，所述外控过载阀的第一控制端与所述有杆腔连接油口之间连接有第一端先导控制油路，所述外控过载阀的第二控制端与所述油缸类型选择阀的工作油口连接；和
控制阀，设置在所述第一端先导控制油路中。
在一些实施方式中，所述控制阀为液控单向阀并设置为使得液压油能够从所述有杆腔连接油口流向所述第一控制端且反向截止，所述液控单向阀的液控端连接至所述无杆腔进回油路以用于反向打开单向阀。
在一些实施方式中，所述控制阀为液控换向阀并包括第一换向阀位和第二换向阀位，所述第一换向阀位设有单向截止阀，所述单向截止阀设置为允许液压油从所述有杆腔连接油口流向所述第一控制端且反向截止，所述第二换向阀位为油路导通位，所述液控换向阀的液控端连接至所述无杆腔进回油路以用于切换至所述第二换向阀位。
在一些实施方式中，所述多路换向阀包括：
有杆腔进回油路，与所述有杆腔连接油口相连并用于连接至各个油缸的有杆腔；
主单向阀，设置在所述有杆腔进回油路中并设置为允许液压油从所述有杆腔连接油口流向有杆腔且反向截止；
其中，所述主单向阀通过先导油路连接至所述无杆腔进回油路以用于 反向打开所述主单向阀。
在一些实施方式中，所述外控过载阀的第一控制端为设有压缩弹簧的弹簧控制端。
在一些实施方式中，所述多路换向阀包括：
主溢流阀，设置在所述主进油口与所述主回油口之间；
其中，所述外控过载阀的第一控制端的压缩弹簧的设定弹簧压力小于所述主溢流阀的设定溢流压力。
在一些实施方式中，所述油缸类型选择阀的工作油口包括与垂直油缸的无杆腔相连的第一工作油口以及与水平油缸的无杆腔相连的第二工作油口，所述油缸类型选择阀用于将一侧的所述进油口选择性切换连接至另一侧的所述第一工作油口或所述第二工作油口，所述外控过载阀与所述第一工作油口或第二工作油口相连。
在一些实施方式中，若干所述油缸类型选择阀包括：
双油缸类型选择阀，所述双油缸类型选择阀的所述第一工作油口连接至所述垂直油缸的无杆腔，且所述第二工作油口连接至所述水平油缸的无杆腔；
单油缸类型选择阀，所述单油缸类型选择阀的所述第一工作油口连接至所述垂直油缸的无杆腔，且所述第二工作油口截止；
其中，所述外控过载阀的第二控制端与所述双油缸类型选择阀的所述第二工作油口相连，并且所述外控过载阀的第二控制端与所述单油缸类型选择阀的所述第一工作油口相连。
在一些实施方式中，所述外控过载阀与所述油缸类型选择阀的所述第一工作油口或第二工作油口相连的连接油路中设有单向保压阀，所述单向保压阀设置为使得液压油能够从所述油缸类型选择阀流向所述外控过载阀且反向截止。
根据本申请的第二方面，提供了一种支腿油缸控制系统，包括支腿油 缸组和上述的多路换向阀，所述多路换向阀用于液压控制所述支腿油缸组。
在一些实施方式中，所述支腿油缸组包括四组侧向支腿油缸组和一一对应地控制四组所述侧向支腿油缸组的四个所述油缸类型选择阀，每组所述侧向支腿油缸组包括垂直油缸和水平油缸，每个所述述油缸类型选择阀用于将所述无杆腔进回油路切换连接至相应的所述侧向支腿油缸组内的垂直油缸的无杆腔或水平油缸的无杆腔中。
在一些实施方式中，所述垂直油缸的工作油路中设有双向液压锁。
根据本申请的第三方面，提供了一种汽车起重机，所述汽车起重机包括上述的支腿油缸控制系统。
在本申请的多路换向阀、支腿油缸控制系统中，在外控过载阀的第一端先导控制油路中增设了控制阀，以开关控制方式实现外控过载阀的保压功能或卸荷功能。控制阀具有单向截止功能，当有杆腔进回油路失压后，外控过载阀的第一端先导控制油路的压力将被保持，外控过载阀将保持关闭状态，从而保证水平缸保持在原来的位置。因此，能够很好地解决垂直油缸回缩到位且伸缩功能选择阀回中位后，水平油缸出现同步回缩现象，从而提升了支腿系统的控制独立性，垂直油缸和水平油缸不产生联动，支腿系统的操纵可靠性和用户满意度得到大大提升。
本申请实施方式的其它特征和优点将在随后的具体实施方式部分予以详细说明。
附图说明
附图是用来提供对本发明实施方式的进一步理解，并且构成说明书的一部分，与下面的具体实施方式一起用于解释本发明实施方式，但并不构成对本发明实施方式的限制。对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。在附图中：
图1为根据本申请的具体实施方式的多路换向阀的液压结构图；
图2为根据本申请的第一实施方式的支腿油缸控制系统的液压原理图，其中采用了图1所示的多路换向阀且各联均处于中位；
图3为图2所示的支腿油缸控制系统在执行缩垂直油缸动作时的液压原理图；
图4为图2所示的支腿油缸控制系统在执行伸水平油缸动作时的液压原理图；
图5为两位两通的液控换向阀的液压结构图；和
图6为根据本申请的第二实施方式的支腿油缸控制系统的液压原理图。
附图标记说明
1.1   伸缩功能选择阀     1.2-1.6 油缸类型选择阀
2     主单向阀           3.1-3.5 双向液压锁
6     主溢流阀           4.1-4.5 垂直油缸
7     外控过载阀         5.1-5.4 水平油缸
9     控制阀             8.1-8.5 单向保压阀
P     主进油口           T       主回油口
c     有杆腔连接油口     e       无杆腔连接油口
L0    有杆腔进回油路     L1      无杆腔进回油路
L2    垂直油缸有杆腔油路 L3      水平油缸有杆腔油路
具体实施方式
以下结合附图对本申请的具体实施方式进行详细说明。应当理解的是，此处所描述的具体实施方式仅用于说明和解释本申请，并不用于限制本申请。
下面参考附图描述根据本申请的多路换向阀、支腿油缸控制系统和汽车起重机。
多路换向阀在工程机械中运用非常广泛，作为示例，下文的实施方式中的多路换向阀及支腿油缸控制系统主要用于控制汽车起重机的水平支腿油缸(简称水平油缸)和垂直支腿油缸(简称垂直油缸)。
本申请公开了一种新型的多路换向阀。如图1所示，在一种具体实施方式中，该多路换向阀包括：
伸缩功能选择阀1.1，包括一侧的主进油口P、主回油口T和另一侧的有杆腔连接油口c、无杆腔连接油口e；
若干油缸类型选择阀，各个油缸类型选择阀的一侧的进油口并联连接至与无杆腔连接油口e相连的无杆腔进回油路L1，油缸类型选择阀的另一侧的工作油口用于连接至无杆腔；
外控过载阀7，与油缸类型选择阀的工作油口相连并用于工作油口的保压或卸荷，外控过载阀7的第一控制端与有杆腔连接油口c之间连接有第一端先导控制油路，外控过载阀7的第二控制端与油缸类型选择阀的工作油口连接；和
控制阀9，设置在第一端先导控制油路中。
本实施方式的多路换向阀可用于控制汽车起重机的支腿系统，如图3所示，应用于支腿油缸控制系统中。其中，伸缩功能选择阀1.1选择伸出或回缩功能，即图1所示的伸缩功能选择阀1.1的上阀位为控制支腿油缸执行伸出动作，且下阀位用于控制支腿油缸执行回缩动作。油缸类型选择阀1.2-1.6用于选择相应的垂直油缸或水平油缸来执行伸缩功能选择阀1.1所选择的伸出或回缩功能。
具体地，参见图1，压力油从主进油口P进入伸缩功能选择阀1.1，伸缩功能选择阀1.1的左侧具有a1、a2和f三个油口，右侧具有b、c和f三个工作油口，即图1所示的伸缩功能选择阀1.1为三位六通换向阀，但此处仅为举例，本申请的伸缩功能选择阀1.1不限于此，也可以是其他多位多通换向阀。伸缩功能选择阀1.1右侧的有杆腔连接油口c连接有有杆腔进回油 路L0，且无杆腔连接油口e连接有无杆腔进回油路L1，多个油缸类型选择阀1.2-1.6的进油口并联至无杆腔进回油路L1，通过油缸类型选择阀的阀位切换，将无杆腔进回油路L1的液压油与相应的水平油缸或垂直油缸的无杆腔连通。
其中，油缸类型选择阀的其中一个工作油口连接有外控过载阀7，用于在油缸无杆腔的油压过大时进行卸荷。为减少电磁开关控制的数量，外控过载阀7一般采用液控方式，如图1所示，外控过载阀7的第一控制端与有杆腔连接油口c相连，外控过载阀7的第二控制端与油缸类型选择阀的工作油口连接。
可见，多路换向阀包括伸缩功能选择阀1.1、多个油缸类型选择阀1.2-1.6和外控过载阀7等基本阀件。在应用于图3的支腿油缸控制系统时，若汽车起重机处于施工状态，垂直油缸4.1-4.5(包括左右两侧共四个垂直油缸以及驾驶室下方的第五垂直油缸)处于活塞杆伸出状态，水平油缸5.1-5.4(包括左右两侧共四个水平油缸)处于伸出状态。在此情况下，若需要调整垂直油缸4.1-4.5或水平油缸5.1-5.4的伸出位置，在调整油缸位置时要求各油缸之间不得相互影响或产生误动作。例如，需要将水平油缸5.1-5.4伸出到某一位置时，则将伸缩功能选择阀1.1切换至对应于伸出动作的上阀位，油缸类型选择阀1.3-1.6切换至对应于水平油缸的下阀位。压力油从P口进入伸缩功能选择阀1.1左侧的a1、a2油口，此时a2口与e口连通，压力油到达无杆腔进回油路L1，进而到达油缸类型选择阀1.3-1.6的进油口s2-s5，此时经过下阀位，油缸类型选择阀1.3-1.6内s1-v1、s2-v2、s3-v3、s4-v4、s5-v5的内油道连通，然后分别通过各自的水平油缸有杆腔油路L3流入相应的水平油缸5.1-5.4的无杆腔。同时，压力油流入外控过载阀7的进口w，当进口压力超过外控过载阀7的设定压力时，外控过载阀7打开，起到过载保护作用。此时水平油缸5.1-5.4的有杆腔油液经有杆腔进回油路L0回油至伸缩功能选择阀1.1的右侧c口，c-f内流道连通，最后流回T口。
当需要将垂直油缸4.1-4.5完全缩回时，压力油从P口进入伸缩功能选择阀1.1的左侧油口a1、a2，伸缩功能选择阀1.1切换至对应于回缩功能的下阀位，此时a2与c相通，e与f相通，压力油通过伸缩功能选择阀1.1的a2口至c口，油液经有杆腔进回油路L0流入水平油缸5.1-5.4的有杆腔。在c口与n口相通的情况下，外控过载阀7的左侧控制腔压力与P口相等，使得外控过载阀7完全关闭，水平油缸5.1-5.4的无杆腔在超过外控过载阀7的设定压力时，也不会出现水平油缸同步回缩现象。
此时，操纵油缸类型选择阀1.2-1.6，使之处于对应垂直油缸的上阀位，即t1-s1、t2-s2、t3-s3、t4-s4、t5-s5相通，垂直油缸4.1-4.5的无杆腔中的油液便可通过油缸类型选择阀1.2-1.6由r1-t2-s2-e、r2-t3-s3-e、r3-t4-s4-e、r4-t5-s5-e，并经伸缩功能选择阀1.1右侧的e-f-T口，由T口回油。当垂直油缸4.1-4.5回缩到位后，伸缩功能选择阀1.1回中位，此时c、e与f相通，c、e连通卸荷，而水平油缸5.1-5.4的有杆腔油液被有杆腔进回油路L0中的主单向阀2的单向截止功能锁定在管路内，无法释放，各个有杆腔保持高压。之前加载至外控过载阀7的控制腔e-n因伸缩功能选择阀1.1回中位卸荷，从而使外控过载阀7的进口w与d1、d2、d3、d4、d5的压力仅能维持在其设定压力。这样，有杆腔的油压大于无杆腔的油压，无杆腔内的油液便由v2-d2-w、v3-d3-w、v4-d4-w、v5-d5-w经外控过载阀7流至T口，从而导致水平油缸5.1-5.4出现回缩现象。
可见，在垂直油缸4.1-4.5回缩到位后，伸缩功能选择阀1.1手柄回中位时，在外控过载阀7的第一端先导控制油路保持一直畅通的情况下，即c口与n口保持一直连通的情况下，水平油缸5.1-5.4会因为有杆腔内油压产生的作用力大于无杆腔内的油压作用力而出现自动回缩问题，从而存在单独控制垂直油缸时，水平油缸产生伴随移动伸缩现象，这对于操作感受、客户体验度和支腿系统的安全稳定性都不利。
因此特别地，本申请在第一端先导控制油路中增设了控制阀9，以开关 控制方式实现外控过载阀7的保压功能或卸荷功能。因控制阀9具有单向截止功能，所以当有杆腔进回油路L0失压后，外控过载阀7的第一端先导控制油路的压力将被保持，外控过载阀7将保持关闭状态，从而保证水平缸5.1-5.4保持在原来的位置。这样就能够很好地解决垂直油缸回缩到位后，且伸缩功能选择阀回中位后，水平油缸出现同步回缩现象。
在图1至图3的实施方式中，控制阀9采用液控单向阀并设置为使得液压油能够从有杆腔连接油口c流向第一控制端且反向截止，液控单向阀的液控端连接至无杆腔进回油路L1以用于反向打开单向阀。
在图5、图6的实施方式中，控制阀9采用液控换向阀并包括第一换向阀位(图5所示的左阀位)和第二换向阀位(图5所示的右阀位)，第一换向阀位的内部油道km中设有单向截止阀，单向截止阀设置为允许液压油从有杆腔连接油口c流向第一控制端且反向截止，第二换向阀位为油路导通位，即第二换向阀位时的内部油道km始终畅通。液控换向阀的液控端l连接至无杆腔进回油路L1(即e口)，无杆腔进回油路L1或e口的压力油进入液控端l时，可促使液控换向阀的阀芯切换至第二换向阀位。
无论是采用液控单向阀还是液控换向阀，甚至其他阀形式，通过在伸缩功能选择阀1.1的右侧c口至外控过载阀7的第一控制端之间增设一个反向截止功能的液控单向阀或具有单向截止功能的二位二通换向阀后，可实现对外控过载阀7控制腔的压力锁定功能，并在需要释放，将控制腔卸荷。如此，一旦垂直油缸4.1-4.5缩到位后，伸缩功能选择阀1.1的操控手柄回中位时，水平油缸5.1-5.4能保持原有位置不变，防止因油缸有杆腔内油压产生的作用力大于无杆腔内的油压作用力而出现伴随性的自动回缩问题，以下还将具体阐述。
需要说明的是，多路换向阀包括主溢流阀6，设置在主进油口P与主回油口T之间。同时，外控过载阀7的第一控制端为设有压缩弹簧的弹簧控制端。外控过载阀7用于对水平油缸及垂直油缸4.5进行过载保护。特别地， 外控过载阀7的第一控制端的压缩弹簧的设定弹簧压力小于主溢流阀6的设定溢流压力。在本文的实施方式中，外控过载阀7的设定弹簧压力为7MPa，而主溢流阀6的设定溢流压力20MPa。
在图1所示的实施方式中，多路换向阀包括：
有杆腔进回油路L0，与有杆腔连接油口c相连并用于连接至各个油缸的有杆腔；
主单向阀2，设置在有杆腔进回油路L0中并设置为允许液压油从有杆腔连接油口c流向有杆腔且反向截止；
其中，主单向阀2通过先导油路连接至无杆腔进回油路L1以用于反向打开主单向阀2。
主单向阀2的设置，可确保在需要时对油缸有杆腔的保压，或者在需要时被反向开启，从而保障有杆腔进回油路L0畅通，确保有杆腔顺利卸荷。
参见图3，油缸类型选择阀的工作油口包括与垂直油缸的无杆腔相连的第一工作油口(例如t2油口)以及与水平油缸的无杆腔相连的第二工作油口(例如v2油口)，油缸类型选择阀用于将一侧的进油口选择性切换连接至另一侧的第一工作油口或第二工作油口，外控过载阀7与第一工作油口或第二工作油口相连。
在图1中，油缸类型选择阀有5联，分别对应于四组侧边支腿油缸组和第五垂直油缸。因此，油缸类型选择阀分为两类，即油缸类型选择阀包括：
双油缸类型选择阀，双油缸类型选择阀的第一工作油口连接至垂直油缸的无杆腔，且第二工作油口连接至水平油缸的无杆腔；
单油缸类型选择阀，单油缸类型选择阀的第一工作油口连接至垂直油缸的无杆腔，且第二工作油口截止；
其中，外控过载阀7的第二控制端与双油缸类型选择阀的第二工作油口相连，并且外控过载阀7的第二控制端与单油缸类型选择阀的第一工作 油口相连。
显然，在应用于图2至图4、图6所示的支腿油缸控制系统时，支腿油缸控制系统包括支腿油缸组和上述的多路换向阀，多路换向阀用于液压控制支腿油缸组。
此时，油缸类型选择阀1.3-1.6为双油缸类型选择阀，用于控制四组侧边支腿油缸组，油缸类型选择阀1.2为单油缸类型选择阀，用于控制第五垂直油缸。双油缸类型选择阀在上下阀位进行切换时，可将无杆腔进回油路L1切换连接于垂直油缸有杆腔油路L2或水平油缸有杆腔油路L3。具体地，本文图示的支腿油缸组包括四组侧向支腿油缸组和一一对应地控制四组侧向支腿油缸组的四个油缸类型选择阀，每组侧向支腿油缸组包括垂直油缸和水平油缸，每个油缸类型选择阀用于将无杆腔进回油路切换连接至相应的侧向支腿油缸组内的垂直油缸的无杆腔或水平油缸的无杆腔中。
图示的单油缸类型选择阀，即油缸类型选择阀1.2，仅具有上阀位为连通位，中位和下位均为截止位，即仅在切换至上阀位时用于控制垂直油缸4.5。另外，垂直油缸的工作油路中设有双向液压锁3.1-3.5，用于油缸保压。
另外，外控过载阀7与油缸类型选择阀的第一工作油口或第二工作油口相连的连接油路中设有单向保压阀8.1-8.5，以防止各水平油缸相互影响，单向保压阀8.1-8.5设置为使得液压油能够从油缸类型选择阀1.2-1.6流向外控过载阀7且反向截止。
可见，本申请的多路换向阀及支腿油缸控制系统，结构简单，具有安全可靠等优点。通过一路伸缩功能选择阀及五路油缸类型选择阀，实现对九个支腿油缸的伸缩控制，同时具有安全保护功能及过载保护，主单向阀2能有效防止水平油缸在汽车起重机在行驶过程中甩出，外控过载阀7及其控制阀9的组合油路，能防止垂直油缸收回后且伸缩功能选择阀杆回中位后，因压力差导致水平油缸自动回缩的问题。
以下结合附图阐述多路换向阀的具体工作过程。
如图3所示，为执行缩垂直油缸动作的过程：
①将油缸类型选择阀1.2-1.6切换至对应于垂直油缸的上阀位，此时s1-t1、S2-t2、s3-t3、s4-t4、s5-t5连通。
②将伸缩功能选择阀1.1切换至执行回缩功能的下阀位，此时a2-c连通、e-f连通。
③油液由P口至a2，通过伸缩功能选择阀1.1到c口,经过设有主单向阀2的有杆腔进回油路L0后进入到各个水平油缸5.1-5.4的有杆腔，同时到达双向液压锁3.1-3.5各自对应的q1-q5口，并把r1-r5所对应的油路反向打开。双向液压锁3.1-3.5对应q1-q5口单向开启后，油液进入到垂直油缸4.1-4.5的有杆腔，即有杆腔进油。
同时，c口的油到k口，打开控制阀9后经m口到外控过载阀7的控制腔n，此时c口的压力将加载至控制腔n。
④垂直油缸4.1-4.5的无杆腔至油缸类型选择阀1.2-1.6对应的t1-t5连通，t1-s1-e-f-T、t2-s2-e-f-T、t3-s3-e-f-T、t4-s4-e-f-T、t5-s5-e-f-T连通，即无杆腔通过无杆腔进回油路L1回油。
⑤有杆腔进油，无杆腔回油，垂直油缸4.1-4.5回缩。当油缸回缩到极限位置时，压力升高到主溢流阀6的设定压力。
⑥将伸缩功能选择阀1.1切换至中位机能。回中位后e、c与f连通卸荷，此时主单向阀2，h口至油缸有杆腔的油被主单向阀2锁止，同时因h口至有杆腔之间为橡胶软管充当蓄能器的作用，因此在很长一段时间仍将保持主溢流阀6所设定的压力。
⑦将油缸类型选择阀1.2-1.6切换至中位机能。此时s1-t1、S2-t2、s3-t3、s4-t4、s5-t5断开。
在外控过载阀7的控制腔增加了控制阀9后，利用液控单向阀的反向截止功能，能保证外控过载阀7的第一端控制腔n始终保持主溢流阀6所设定的压力，因此即使伸缩功能选择阀1.1切换至中位机能后外控过载阀7 仍能有效关闭，不得产生溢流。水平油缸5.1-5.4的无杆腔内的油液保持在v2-d2-w、v3-d3-w、v4-d4-w、v5-d5-w之间，垂直油缸4.5无杆腔的油液保持在r5-t1-d1-w之间,压力基本保持不变。由此可见，水平油缸5.1-5.4有杆腔内的油被主单向阀2锁止及无杆腔内的油被外控过载阀7锁止，有杆腔及无杆腔的压力基本保持不变，因此油缸位置保持不变，不会因垂直油缸缩回后选择阀杆回中导致水平油缸回缩。
如图4所示，支腿油缸控制系统在执行伸水平油缸动作的过程。
①将油缸类型选择阀1.3-1.6切换至对应水平油缸的下阀位，此时s2-v2、s3-v3、s4-t4、s5-t5连通。
②将伸缩功能选择阀1.1切换至实现伸出功能的上阀位，此时a2-e连通、c-f连通。
③油液由P口至a2，通过伸缩功能选择阀1.1到e口,无杆腔进回油路L1通压力油，分别与s1、s2、s3、s4、s5相通，经油缸类型选择阀1.3-1.6到达v2、v3、v4、v5,然后到达水平油缸1.2-1.6的无杆腔，同时打开单向保压阀8.2-8.5到达外控过载阀7的进口w。此时e口过来的油液通过el先导油路反向打开控制阀9，通过ej先导油路反向打开主单向阀2；h-g连通，有杆腔进回油路L0回油，水平油缸5.1-5.4的有杆腔的油液由无杆腔-h-g-c-f-T流回，即水平油缸5.1-5.4回油；n-m-k-c-f-T连通，外控过载阀7的控制腔n卸荷。
④当水平油缸5.1-5.4的无杆腔进油伸出时，油液同时由v2-d2-w、v3-d3-w、v4-d4-w、v5-d5-w，而此时外控过载阀7的控制腔因控制阀9反向打开卸荷，因此外控过载阀7进口w压力超过过载阀设定压力时便可打开溢流，实现对水平油缸5.1-5.4的过载保护。
如图6所示，在另一实施方式中，通过采用一个二位二通换向阀代替图2中的作为液控单向阀的控制阀9。当垂直油缸4.1-4.5的有杆腔或水平油缸5.1-5.4有杆腔进油时，P口的油液通过由a2-c-g经主单向阀2，从h 口至有杆腔，同时控制油从c口至k口经过作为二位二通换向阀的控制阀9内左位的单向阀后，到达外控过载阀7的控制腔n,保证外控过载阀7的控制腔n保持高压，即使伸缩功能选择阀1.1回中位后，因二位二通换向阀的单向锁止功能，仍然能将该控制腔高压锁定。因此当垂直油缸4.1-4.5缩回后，水平油缸5.1-5.4不会因外控过载阀7的控制腔失压而出现回缩现象。
当伸缩功能选择阀1.1切换至缩对应位置时，压力油通过el先导油路可将二位二通换向阀切换至右位连通状态，外控过载阀7的控制腔的油液通过n-m-k-c油路，经过伸缩功能选择阀1.1的c-f通道，经T口卸荷。此时外控过载阀7的端部压力为其设定弹簧压力，可实现对水平油缸5.1-5.4的过载保护。
此外，本申请还保护一种汽车起重机，包括上述的支腿油缸控制系统。本申请的汽车起重机具有更好的操纵性能，其支腿系统不会阐述垂直油缸和水平油缸的联动状况，提升了产品性能。
在本申请的描述中，需要理解的是，术语“第一”、“第二”仅用于描述目的，而不能理解为指示或暗示相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。在本申请的描述中，“多个”的含义是至少两个，例如两个，三个等，除非另有明确具体的限定。
在本申请中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”、“固定”等术语应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或成一体；可以是机械连接，也可以是电连接或彼此可通讯；可以是直接相连，也可以通过中间媒介间接相连，可以是两个元件内部的连通或两个元件的相互作用关系，除非另有明确的限定。对于本领域的普通技术人员而言，可以根据具体情况理解上述术语在本申请中的具体含义。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特 征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
尽管上面已经示出和描述了本申请的实施例，可以理解的是，上述实施例是示例性的，不能理解为对本申请的限制，本领域的普通技术人员在本申请的范围内可以对上述实施例进行变化、修改、替换和变型。

Claims (13)

  1. 一种多路换向阀，其特征在于，所述多路换向阀包括：
    伸缩功能选择阀(1.1)，包括一侧的主进油口(P)、主回油口(T)和另一侧的有杆腔连接油口(c)、无杆腔连接油口(e)；
    若干油缸类型选择阀，各个所述油缸类型选择阀的一侧的进油口并联连接至与所述无杆腔连接油口(e)相连的无杆腔进回油路(L1)，所述油缸类型选择阀的另一侧的工作油口用于连接至无杆腔；
    外控过载阀(7)，与所述油缸类型选择阀的工作油口相连并用于所述工作油口的保压或卸荷，所述外控过载阀(7)的第一控制端与所述有杆腔连接油口(c)之间连接有第一端先导控制油路，所述外控过载阀(7)的第二控制端与所述油缸类型选择阀的工作油口连接；和
    控制阀(9)，设置在所述第一端先导控制油路中。
  2. 根据权利要求1所述的多路换向阀，其特征在于，所述控制阀(9)为液控单向阀并设置为使得液压油能够从所述有杆腔连接油口(c)流向所述第一控制端且反向截止，所述液控单向阀的液控端连接至所述无杆腔进回油路(L1)以用于反向打开单向阀。
  3. 根据权利要求1所述的多路换向阀，其特征在于，所述控制阀(9)为液控换向阀并包括第一换向阀位和第二换向阀位，所述第一换向阀位设有单向截止阀，所述单向截止阀设置为允许液压油从所述有杆腔连接油口(c)流向所述第一控制端且反向截止，所述第二换向阀位为油路导通位，所述液控换向阀的液控端连接至所述无杆腔进回油路(L1)以用于切换至所述第二换向阀位。
  4. 根据权利要求1所述的多路换向阀，其特征在于，所述多路换向阀包括：
    有杆腔进回油路(L0)，与所述有杆腔连接油口(c)相连并用于连接至各个油缸的有杆腔；
    主单向阀(2)，设置在所述有杆腔进回油路(L0)中并设置为允许液压油从所述有杆腔连接油口(c)流向有杆腔且反向截止；
    其中，所述主单向阀(2)通过先导油路连接至所述无杆腔进回油路(L1)以用于反向打开所述主单向阀(2)。
  5. 根据权利要求1所述的多路换向阀，其特征在于，所述外控过载阀(7)的第一控制端为设有压缩弹簧的弹簧控制端。
  6. 根据权利要求5所述的多路换向阀，其特征在于，所述多路换向阀包括：
    主溢流阀(6)，设置在所述主进油口(P)与所述主回油口(T)之间；
    其中，所述外控过载阀(7)的第一控制端的压缩弹簧的设定弹簧压力小于所述主溢流阀(6)的设定溢流压力。
  7. 根据权利要求1～6中任意一项所述的多路换向阀，其特征在于，所述油缸类型选择阀的工作油口包括与垂直油缸的无杆腔相连的第一工作油口以及与水平油缸的无杆腔相连的第二工作油口，所述油缸类型选择阀用于将一侧的所述进油口选择性切换连接至另一侧的所述第一工作油口或所述第二工作油口，所述外控过载阀(7)与所述第一工作油口或第二工作油口相连。
  8. 根据权利要求7所述的多路换向阀，其特征在于，若干所述油缸类 型选择阀包括：
    双油缸类型选择阀，所述双油缸类型选择阀的所述第一工作油口连接至所述垂直油缸的无杆腔，且所述第二工作油口连接至所述水平油缸的无杆腔；
    单油缸类型选择阀，所述单油缸类型选择阀的所述第一工作油口连接至所述垂直油缸的无杆腔，且所述第二工作油口截止；
    其中，所述外控过载阀(7)的第二控制端与所述双油缸类型选择阀的所述第二工作油口相连，并且所述外控过载阀(7)的第二控制端与所述单油缸类型选择阀的所述第一工作油口相连。
  9. 根据权利要求7所述的多路换向阀，其特征在于，所述外控过载阀(7)与所述油缸类型选择阀的所述第一工作油口或第二工作油口相连的连接油路中设有单向保压阀，所述单向保压阀设置为使得液压油能够从所述油缸类型选择阀流向所述外控过载阀(7)且反向截止。
  10. 一种支腿油缸控制系统，其特征在于，所述支腿油缸控制系统包括支腿油缸组和根据权利要求1～9中任意一项所述的多路换向阀，所述多路换向阀用于液压控制所述支腿油缸组。
  11. 根据权利要求10所述的支腿油缸控制系统，其特征在于，所述支腿油缸组包括四组侧向支腿油缸组和一一对应地控制四组所述侧向支腿油缸组的四个所述油缸类型选择阀，每组所述侧向支腿油缸组包括垂直油缸和水平油缸，每个所述述油缸类型选择阀用于将所述无杆腔进回油路切换连接至相应的所述侧向支腿油缸组内的垂直油缸的无杆腔或水平油缸的无杆腔中。
  12. 根据权利要求10所述的支腿油缸控制系统，其特征在于，垂直油缸的工作油路中设有双向液压锁。
  13. 一种汽车起重机，其特征在于，所述汽车起重机包括根据权利要求10～12中任意一项所述的支腿油缸控制系统。
PCT/CN2023/136157 2023-07-04 2023-12-04 多路换向阀、支腿油缸控制系统和汽车起重机 Ceased WO2025007488A1 (zh)

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