CN210565409U - Crane with a movable crane - Google Patents
Crane with a movable crane Download PDFInfo
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- CN210565409U CN210565409U CN201921444209.1U CN201921444209U CN210565409U CN 210565409 U CN210565409 U CN 210565409U CN 201921444209 U CN201921444209 U CN 201921444209U CN 210565409 U CN210565409 U CN 210565409U
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Abstract
The utility model discloses a crane, including jib loading boom and hydraulic system, hydraulic system includes the flexible hydro-cylinder that is used for making the jib loading boom flexible and is used for the variable amplitude hydro-cylinder that becomes the width of cloth to the jib loading boom, and hydraulic system includes: a hydraulic pump; the oil tank is used for providing hydraulic oil for the hydraulic pump; the first reversing valve comprises a first telescopic working oil port communicated with the first cavity of the telescopic oil cylinder, a second telescopic working oil port communicated with the second cavity of the telescopic oil cylinder, a telescopic oil inlet communicated with the hydraulic pump and a telescopic oil return port communicated with the oil tank; the second reversing valve comprises a first amplitude-variable working oil port communicated with the first cavity of the amplitude-variable oil cylinder, a second amplitude-variable working oil port communicated with the second cavity of the amplitude-variable oil cylinder, an amplitude-variable oil inlet communicated with the hydraulic pump and an amplitude-variable oil return port communicated with the oil tank; the electric proportional speed regulating valve comprises an oil inlet communicated with the hydraulic pump, an oil outlet communicated with the telescopic oil inlet and the amplitude variable oil inlet, and an electric proportional control end.
Description
Technical Field
The utility model relates to an engineering machine tool field, in particular to hoist.
Background
In the engineering machinery industry, a crane almost does not leave a hydraulic transmission technology, the stretching and amplitude variation of a crane arm used in hoisting operation are realized, and the driving control is realized by using a hydraulic oil cylinder, such as a stretching oil cylinder 1 'and an amplitude variation oil cylinder 2' shown in a hydraulic schematic diagram of fig. 1. The valve used for controlling the action of two or more than two executing elements is commonly called a multi-way valve, and the multi-way valve controlled by proportional throttling is mostly used on crane products and is used for the actions of stretching, amplitude changing, lifting, rotation and the like. As shown in fig. 1, the telescopic cylinder 1 'and the luffing cylinder 2' are controlled by a multi-way valve 3 ', and the multi-way valve 3' comprises two electric proportional control reversing valves respectively for proportional control of the telescopic cylinder 1 'and the luffing cylinder 2'. For the multi-way valve 3' shown in the figure, 4 electric proportional control ends of the multi-way valve are needed for controlling the amplitude variation and the telescopic action of the crane boom, a plurality of electro-hydraulic elements are needed, a plurality of proportional control ports of electric signals are needed, the control structure is complex, and the cost is high; meanwhile, when the electric proportional control reversing valve is used for electric proportional control, oil entering the telescopic oil cylinder 1 'and the amplitude-variable oil cylinder 2' and return oil coming out of the telescopic oil cylinder 1 'and the amplitude-variable oil cylinder 2' need to pass through the electric proportional control valve, throttling loss exists in the oil inlet and the return oil, and the system is large in pressure loss, high in heat production and poor in energy conservation.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to provide a crane, its system simple structure, hydraulic system loss of pressure is little.
The utility model discloses a crane, including jib loading boom and hydraulic system, hydraulic system is including being used for stretching out and drawing back the flexible hydro-cylinder of jib loading boom with be used for right the jib loading boom becomes the width of cloth hydro-cylinder that becomes of width, hydraulic system includes:
a hydraulic pump;
the oil tank is used for providing hydraulic oil for the hydraulic pump;
the first reversing valve comprises a first telescopic working oil port communicated with a first cavity of the telescopic oil cylinder, a second telescopic working oil port communicated with a second cavity of the telescopic oil cylinder, a telescopic oil inlet communicated with the hydraulic pump and a telescopic oil return port communicated with the oil tank, wherein in a first working state of the telescopic oil cylinder, the first telescopic working oil port is communicated with the telescopic oil inlet, the second telescopic working oil port is communicated with the telescopic oil return port, in a second working state of the telescopic oil cylinder, the first telescopic working oil port is communicated with the telescopic oil return port, and the second telescopic working oil port is communicated with the telescopic oil inlet;
the second reversing valve comprises a first amplitude-variable working oil port communicated with the first cavity of the amplitude-variable oil cylinder, a second amplitude-variable working oil port communicated with the second cavity of the amplitude-variable oil cylinder, an amplitude-variable oil inlet communicated with the hydraulic pump and an amplitude-variable oil return port communicated with the oil tank, wherein in a first working state of the amplitude-variable oil cylinder, the first amplitude-variable working oil port is communicated with the amplitude-variable oil inlet, the second amplitude-variable working oil port is communicated with the amplitude-variable oil return port, and in a second working state of the amplitude-variable oil cylinder, the first amplitude-variable working oil port is communicated with the amplitude-variable oil return port, and the second amplitude-variable working oil port is communicated with the amplitude-variable oil inlet;
the electric proportional speed regulating valve comprises an oil inlet communicated with the hydraulic pump, an oil outlet communicated with the telescopic oil inlet and the variable amplitude oil inlet, and an electric proportional control end.
In some embodiments, the first and/or second direction valve is a manual direction valve.
In some embodiments, the first and/or second directional valves are manual, electric, double control directional valves.
In some embodiments of the present invention, the,
the first cavity of the telescopic oil cylinder is a rodless cavity, the second cavity of the telescopic oil cylinder is a rod cavity, the hydraulic system further comprises a first balance valve with a first valve position and a second valve position, the first telescopic working oil port and the first cavity are connected through a one-way valve at the first valve position of the first balance valve, the first telescopic working oil port and the first cavity are connected through a throttle valve at the second valve position of the first balance valve, the first balance valve is further provided with a spring control end enabling the balance valve to tend to be switched to the first valve position and a hydraulic control end enabling the first balance valve to tend to be switched to the second valve position, and the hydraulic control end is communicated with the second cavity; and/or the presence of a gas in the gas,
the hydraulic system comprises a first chamber of the variable amplitude oil cylinder, a second chamber of the variable amplitude oil cylinder, a first balance valve, a first variable amplitude working oil port, a second balance valve and a balance valve, wherein the first chamber of the variable amplitude oil cylinder is a rodless chamber, the second chamber of the variable amplitude oil cylinder is a rod chamber, the first balance valve is provided with a first valve position and a second valve position, the first variable amplitude working oil port is connected with the first chamber through a one-way valve at the first valve position of the second balance valve, the first variable amplitude working oil port is connected with the first chamber through a throttling valve at the second valve position of the second balance valve, the balance valve is further provided with a spring control end enabling the second balance valve to tend to be switched to the first valve position and a hydraulic control end enabling the second balance valve to tend to be switched to the second valve position, and the hydraulic control end.
In some embodiments, the hydraulic system includes an integrated valve body on which the first directional control valve, the second directional control valve, and the electro-proportional governor valve are integrated.
Based on the utility model provides a crane carries out flow control to flexible hydro-cylinder and change width of cloth hydro-cylinder through adopting electric proportional speed control valve, has reduced the electric proportional control end of system, has reduced the controlling element who sets up with electric proportional control end, makes system architecture simpler. Meanwhile, when the telescopic oil cylinder and the variable amplitude oil cylinder are throttled and regulated, return oil from oil outlets of the telescopic oil cylinder and the variable amplitude oil cylinder directly returns to the oil tank without passing through the electric proportional speed regulating valve after passing through the first reversing valve or the second reversing valve, so that throttling loss is hardly generated, and the throttling loss is small compared with that of a hydraulic system in the prior art.
Other features of the present invention and advantages thereof will become apparent from the following detailed description of exemplary embodiments of the invention, which proceeds with reference to the accompanying drawings.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without undue limitation to the invention. In the drawings:
FIG. 1 is a hydraulic schematic diagram of boom telescoping and luffing hydraulic control of a crane of the prior art;
fig. 2 is a hydraulic schematic diagram of the boom extension and luffing hydraulic control of the crane of the utility model.
Detailed Description
The technical solutions in the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only some embodiments of the present invention, not all embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the invention, its application, or uses. Based on the embodiments in the present invention, all other embodiments obtained by a person skilled in the art without creative efforts belong to the protection scope of the present invention.
Unless specifically stated otherwise, the relative arrangement of the components and steps, the numerical expressions, and numerical values set forth in these embodiments do not limit the scope of the present invention. Meanwhile, it should be understood that the sizes of the respective portions shown in the drawings are not drawn in an actual proportional relationship for the convenience of description. Techniques, methods, and apparatus known to those of ordinary skill in the relevant art may not be discussed in detail but are intended to be part of the specification where appropriate. In all examples shown and discussed herein, any particular value should be construed as merely illustrative, and not limiting. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numbers and letters refer to like items in the following figures, and thus, once an item is defined in one figure, further discussion thereof is not required in subsequent figures.
Spatially relative terms, such as "above … …," "above … …," "above … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
The crane comprises a crane boom and a hydraulic system, wherein the hydraulic system comprises a telescopic oil cylinder 1 for stretching the crane boom and a luffing oil cylinder 2 for luffing the crane boom, and the hydraulic system comprises a hydraulic pump, an oil tank, a first reversing valve 5, a second reversing valve 6 and an electric proportional speed regulating valve 7. The hydraulic pump is used for supplying oil to the telescopic oil cylinder 1 and the amplitude variation oil cylinder 2. The oil tank is used for providing hydraulic oil for the hydraulic pump;
the first reversing valve 5 comprises a first telescopic working oil port A1 communicated with a first cavity of the telescopic oil cylinder 1, a second telescopic working oil port B1 communicated with a second cavity of the telescopic oil cylinder 1, a telescopic oil inlet P1 communicated with a hydraulic pump and a telescopic oil return port T1 communicated with an oil tank, wherein in the first working state of the telescopic oil cylinder 1, the first telescopic working oil port A1 is communicated with a telescopic oil inlet P1, the second telescopic working oil port B1 is communicated with a telescopic oil return port T1, and in the second working state of the telescopic oil cylinder 1, the first telescopic working oil port A1 is communicated with a telescopic oil return port T1, and the second telescopic working oil port B1 is communicated with a telescopic oil inlet P1; as shown in fig. 2, the first direction valve 5 may be a three-position four-way direction valve, and when the hydraulic pump supplies oil to the telescopic cylinder 1, the telescopic cylinder 1 is switched to the left valve position by the first direction valve 5 to have a first working state, and the telescopic cylinder 1 is switched to the second working state by the first direction valve 5 to be switched to the right valve position. As shown in fig. 2, the first direction valve 5 further has a middle valve position, and when the first direction valve 5 is switched to the middle valve position, the first telescopic working oil port a1 is closed from the telescopic oil inlet P1, and the second telescopic working oil port B1 is communicated with the telescopic oil return port T1.
The second reversing valve 6 comprises a first variable amplitude working oil port A2 communicated with a first cavity of the variable amplitude oil cylinder 2, a second variable amplitude working oil port B2 communicated with a second cavity of the variable amplitude oil cylinder 2, a variable amplitude oil inlet P2 communicated with the hydraulic pump and a variable amplitude oil return port T2 communicated with the oil tank, in the first working state of the variable amplitude oil cylinder 2, the first variable amplitude working oil port A2 is communicated with the variable amplitude oil inlet P2, the second variable amplitude working oil port B2 is communicated with the variable amplitude oil return port T2, in the second working state of the variable amplitude oil cylinder 2, the first variable amplitude working oil port A2 is communicated with the variable amplitude oil return port T2, and the second variable amplitude working oil port B2 is communicated with the variable amplitude oil inlet P2; as shown in fig. 2, the second directional valve 6 may be a three-position four-way directional valve, and when the hydraulic pump supplies oil to the luffing cylinder 2, the luffing cylinder 2 is switched to the left valve position by the second directional valve 6 to have the first working state, and the luffing cylinder 2 is switched to the second working state by the second directional valve 6 to the right valve position. As shown in fig. 2, the second reversing valve 6 further has a middle valve position, when the second reversing valve 6 is switched to the middle valve position, the first luffing working oil port a2 is cut off from the luffing oil inlet P2, and the second luffing working oil port B2 is communicated with the luffing oil return port T2.
The electric proportional speed control valve 7 comprises an oil inlet communicated with the hydraulic pump, an oil outlet communicated with the telescopic oil inlet P1 and the variable-amplitude oil inlet P2, and an electric proportional control end, as shown in FIG. 2, the electric proportional speed control valve 7 regulates the flow passing through the electric proportional speed control valve 7 through the electric proportional control end 71.
The telescopic and amplitude-variable actions of the crane boom are carried out simultaneously, namely the telescopic oil cylinder 1 and the amplitude-variable oil cylinder 2 are rarely simultaneously acted, and when the crane boom is simultaneously stretched and amplitude-variable, the simultaneous stretching and amplitude-variable actions generally occur during no-load hoisting preparation or vehicle collection, and the independent proportional control of the telescopic oil cylinder 1 and the amplitude-variable oil cylinder 2 is generally not needed.
In the crane of the embodiment, when the telescopic cylinder 1 or the luffing cylinder 2 independently operates, proportional flow control can be performed on the telescopic cylinder 1 or the luffing cylinder 2 through the electric proportional speed control valve 7, and when the telescopic cylinder 1 and the luffing cylinder 2 simultaneously operate, common proportional flow control can also be performed. The hydraulic system of the embodiment reduces the electric proportional control end of the system by adopting the electric proportional speed regulating valve 7, the first reversing valve 5 and the second reversing valve 6, reduces the control elements matched with the electric proportional control end, can realize the speed regulation control of the telescopic action of the crane boom and the speed regulation control of the amplitude variation action of the crane boom, and is simpler.
Meanwhile, when the telescopic oil cylinder 1 and the luffing oil cylinder 2 are throttled and regulated, return oil from oil outlets of the telescopic oil cylinder 1 and the luffing oil cylinder 2 directly returns to an oil tank without passing through the electric proportional speed regulating valve 7 after passing through the first reversing valve 5 or the second reversing valve 6, so that throttling loss is hardly generated, and the throttling loss is small compared with that of a hydraulic system in the prior art.
In some embodiments, the first and/or second direction valves 5, 6 are manual direction valves. The manual reversing valve accords with the operation habit of a driver.
In some embodiments, as shown in fig. 2, the first directional valve 5 and/or the second directional valve 6 are manual, electric double control directional valves. As shown in the figure, the first direction valve 5 and the second direction valve 6 are both manual and electric double control direction valves, both ends of the first direction valve 5 and the second direction valve 6 are provided with a manual operation port and an electric operation port, and the valve positions of the first direction valve 5 and the second direction valve 6 can be switched manually or electrically.
In some embodiments, as shown in fig. 2, the first chamber of the telescopic cylinder 1 is a rodless chamber, the second chamber of the telescopic cylinder 1 is a rod chamber, the hydraulic system further includes a first balance valve 3 having a first valve position and a second valve position, in the first valve position, the first telescopic working fluid port a1 is connected with the first chamber through a check valve, as shown in fig. 2, the fluid outlet of the check valve is connected with the first chamber, in the second valve position, the first telescopic working fluid port a1 is connected with the first chamber through a throttle valve, the first balance valve further has a spring control end for making the balance valve tend to switch to the first valve position and a fluid control end for making the first balance valve tend to switch to the second valve position, the fluid control end is communicated with the second chamber; and/or the presence of a gas in the gas,
the first cavity of the amplitude-variable oil cylinder 2 is a rodless cavity, the second cavity of the amplitude-variable oil cylinder 2 is a rod cavity, the hydraulic system further comprises a second balance valve 4 with a first valve position and a second valve position, in the first valve position, the first amplitude-variable working oil port A2 is connected with the first cavity through a one-way valve, the oil outlet of the one-way valve is connected with the first cavity, in the second valve position, the first amplitude-variable working oil port A2 is connected with the first cavity through a throttle valve, the balance valve is further provided with a spring control end enabling the second balance valve to tend to be switched to the first valve position and a hydraulic control end enabling the second balance valve to tend to be switched to the second valve position, and the hydraulic control end is communicated with the second cavity. According to the crane in the embodiment, by arranging the first balance valve 3 and the second balance valve 4, when the rodless cavity of the telescopic oil cylinder 1 or the luffing oil cylinder 2 is filled with oil, namely the crane boom extends out or the crane boom luffs towards the direction of increasing amplitude, the balance valve is in the first valve position, the one-way valve of the balance valve is opened, and the piston rod of the telescopic oil cylinder 1 or the luffing oil cylinder 2 extends out. When the first reversing valve 5 or the second reversing valve 6 switches valve positions, oil enters the rod cavity of the telescopic oil cylinder 1 or the amplitude-variable oil cylinder 2 when oil is reversed, the oil does not enter the rod cavity, oil return of the rod cavity is stopped by the one-way valve when the oil is just reversed, sudden quick retraction or quick reduction of amplitude of the crane boom under the action of gravity can be prevented, and safety protection of the crane boom can be realized. Along with the increase of the oil pressure of the rod cavity of the telescopic oil cylinder 1 or the amplitude-variable oil cylinder 2, the balance valve tends to be switched to the second valve position, the throttling opening of the throttling valve of the balance valve is gradually increased, the oil return channel of the rodless cavity of the telescopic oil cylinder 1 or the amplitude-variable oil cylinder 2 on the balance valve is gradually opened, and the crane boom is safely and reliably retracted or the amplitude is reduced. The balance valve is referred to as a first balance valve 3 or a second balance valve 4.
In some embodiments, the hydraulic system comprises an integrated valve body on which the first directional valve 5, the second directional valve 6 and the electro-proportional governor valve 7 are integrated. This embodiment may make the hydraulic system more compact.
In some embodiments, as shown in FIG. 2, the oil drain port of the electric proportional speed control valve is communicated with the oil tank, and this arrangement facilitates oil drainage of the electric proportional speed control valve.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention and not to limit it; although the present invention has been described in detail with reference to preferred embodiments, it should be understood by those skilled in the art that: the invention can be modified or equivalent substituted for some technical features; without departing from the spirit of the present invention, it should be understood that the scope of the claims is intended to cover all such modifications and variations.
Claims (5)
1. A crane comprising a boom and a hydraulic system comprising a telescopic cylinder (1) for telescoping the boom and a luffing cylinder (2) for luffing the boom, characterized in that the hydraulic system comprises:
a hydraulic pump;
the oil tank is used for providing hydraulic oil for the hydraulic pump;
the first reversing valve (5) comprises a first telescopic working oil port (A1) communicated with a first cavity of the telescopic oil cylinder (1), a second telescopic working oil port (B1) communicated with a second cavity of the telescopic oil cylinder (1), a telescopic oil inlet (P1) communicated with the hydraulic pump and a telescopic oil return port (T1) communicated with the oil tank, wherein in a first working state of the telescopic oil cylinder (1), the first telescopic working oil port (A1) is communicated with the telescopic oil inlet (P1), the second telescopic working oil port (B1) is communicated with the telescopic oil return port (T1), in a second working state of the telescopic oil cylinder (1), the first telescopic working oil port (A1) is communicated with the telescopic oil return port (T1), and the second telescopic working oil port (B1) is communicated with the telescopic oil inlet (P1);
the second reversing valve (6) comprises a first amplitude-variable working oil port (A2) communicated with the first cavity of the amplitude-variable oil cylinder (2), a second amplitude-variable working oil port (B2) communicated with the second cavity of the amplitude-variable oil cylinder (2), an amplitude-variable oil inlet (P2) communicated with the hydraulic pump and an amplitude-variable oil return port (T2) communicated with the oil tank, wherein in the first working state of the amplitude-variable oil cylinder (2), the first amplitude-variable working oil port (A2) is communicated with the amplitude-variable oil inlet (P2), the second amplitude-variable working oil port (B2) is communicated with the amplitude-variable oil return port (T2), in the second working state of the amplitude-variable oil cylinder (2), the first amplitude-variable working oil port (A2) is communicated with the amplitude-variable oil return port (T2), and the second amplitude-variable working oil port (B2) is communicated with the amplitude-variable oil inlet (P2);
the electric proportional speed regulating valve (7) comprises an oil inlet communicated with the hydraulic pump, an oil outlet communicated with the telescopic oil inlet (P1) and the amplitude-variable oil inlet (P2), and an electric proportional control end (71).
2. A crane as claimed in claim 1, characterized in that the first direction valve (5) and/or the second direction valve (6) are manual direction valves.
3. The crane according to claim 1, characterized in that the first directional control valve (5) and/or the second directional control valve (6) are manual, electric double control directional control valves.
4. The crane according to claim 1,
the hydraulic system comprises a first cavity of the telescopic oil cylinder (1), a second cavity of the telescopic oil cylinder (1) and a first balance valve (3) with a first valve position and a second valve position, wherein the first valve position of the first balance valve (3) is provided with a first telescopic working oil port (A1) which is connected with the first cavity through a one-way valve, the second valve position of the first balance valve (3) is provided with a first telescopic working oil port (A1) which is connected with the first cavity through a throttle valve, the first balance valve (3) is further provided with a spring control end which enables the balance valve to tend to be switched to the first valve position and a hydraulic control end which enables the first balance valve (3) to tend to be switched to the second valve position, and the hydraulic control end is communicated with the second cavity; and/or the presence of a gas in the gas,
the hydraulic system comprises a luffing oil cylinder (2), a first cavity of the luffing oil cylinder (2) is a rodless cavity, a second cavity of the luffing oil cylinder (2) is a rod cavity, the hydraulic system further comprises a second balance valve (4) with a first valve position and a second valve position, the first luffing working oil port (A2) is connected with the first cavity through a one-way valve at the first valve position of the second balance valve (4), the first luffing working oil port (A2) is connected with the first cavity through a throttle valve at the second valve position of the second balance valve (4), the balance valve further comprises a spring control end enabling the second balance valve (4) to tend to be switched to the first valve position and a hydraulic control end enabling the second balance valve (4) to tend to be switched to the second valve position, and the hydraulic control end is communicated with the second cavity.
5. The crane according to claim 1, characterized in that the hydraulic system comprises an integrated valve body on which the first directional valve (5), the second directional valve (6) and the electro-proportional governor valve (7) are integrated.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921444209.1U CN210565409U (en) | 2019-09-02 | 2019-09-02 | Crane with a movable crane |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201921444209.1U CN210565409U (en) | 2019-09-02 | 2019-09-02 | Crane with a movable crane |
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| CN210565409U true CN210565409U (en) | 2020-05-19 |
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| CN201921444209.1U Active CN210565409U (en) | 2019-09-02 | 2019-09-02 | Crane with a movable crane |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112814961A (en) * | 2021-01-15 | 2021-05-18 | 三一汽车制造有限公司 | Boom hydraulic system of working vehicle, control method and working vehicle |
| CN114412853A (en) * | 2021-12-31 | 2022-04-29 | 徐州重型机械有限公司 | Double-cylinder-head telescopic system and control method |
-
2019
- 2019-09-02 CN CN201921444209.1U patent/CN210565409U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112814961A (en) * | 2021-01-15 | 2021-05-18 | 三一汽车制造有限公司 | Boom hydraulic system of working vehicle, control method and working vehicle |
| CN112814961B (en) * | 2021-01-15 | 2023-05-30 | 三一汽车制造有限公司 | Boom hydraulic system of working vehicle, control method and working vehicle |
| CN114412853A (en) * | 2021-12-31 | 2022-04-29 | 徐州重型机械有限公司 | Double-cylinder-head telescopic system and control method |
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