Double-combined oil cylinder alternating impact ice-breaking electro-hydraulic control system
Patent Information
- Application Number
- CN202521865151.3
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-09-01
- Publication Date
- 2026-08-21
- Estimated Expiration
- 2035-09-01
AI Technical Summary
[0003]市面上已有的破冰装置没有相应的液压控制系统，不能实现主动振动冲击
[0011] The beneficial effects of this utility model are as follows: This utility model adopts vibration impact de-icing instead of traditional crushing ice breaking, which does not require a heavy equipment weight. The weight is usually only a fraction of that of traditional ice breaking equipment, which can greatly improve the flexibility of equipment operation and relocation; the vibration impact energy is concentrated, making it easier to break the hard ice layer on the road surface, reducing the energy consumption of the equipment while improving the ice breaking efficiency; the two ice breaking composite cylinders alternately impact the road surface, which can not only reduce the impact on the reaction force of the equipment itself, but also better exert the effect of vibration ice breaking.
Smart Images
Figure CN224664927U_ABST
Abstract
Description
Technical Field
[0001] This utility model relates to a control system, and more particularly to a dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system. Background Technology
[0002] In recent years, extreme weather events have frequently caused ice and snow disasters, creating an urgent need for road de-icing equipment that is adjustable in parameters, highly efficient in operation, widely adaptable, and economical.
[0003] Existing ice-breaking devices on the market lack corresponding hydraulic control systems and cannot achieve active vibration impact. Relying on their own weight to crush the ice layer by rolling over the road surface is not only inefficient, but the excessively heavy equipment is also inconvenient to operate and may damage the road surface. Utility Model Content
[0004] This invention aims to at least partially solve one of the technical problems in related technologies. To this end, this invention proposes a dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system.
[0005] The technical solution adopted by this utility model to solve its technical problem is: a dual composite cylinder alternating impact ice-breaking electro-hydraulic control system, including a constant pressure oil source, an electro-hydraulic proportional directional valve and two ice-breaking composite cylinders; each of the ice-breaking composite cylinders includes a vibration cylinder, and the vibration cylinders are all single-rod cylinders; The vibrating cylinder includes a vibrating cylinder barrel, inside which a vibrating piston is provided. The vibrating piston is connected to a vibrating piston rod. The two ends of the vibrating cylinder barrel are respectively connected to a front vibrating cover and a rear vibrating cover. The front vibrating cover is provided with a first vibrating oil port, and the rear vibrating cover is provided with a second vibrating oil port. The first vibrating oil port is connected to the rod chamber of the vibrating cylinder, and the second vibrating oil port is connected to the rodless chamber of the vibrating cylinder. The rodless chamber of the vibrating cylinder is located above the rod chamber of the vibrating cylinder. The first vibration ports of the two ice-breaking composite hydraulic cylinders are respectively connected to the oil supply port of the constant pressure oil source, and the second vibration ports of the two ice-breaking composite hydraulic cylinders are respectively connected to the two control ports of the same electro-hydraulic proportional directional valve. The oil supply port and return port of the electro-hydraulic proportional directional valve are respectively connected to the oil supply port and the return port of the constant pressure oil source.
[0006] In a preferred embodiment of the present invention, an avoidance cylinder is further provided on the upper part of the vibration cylinder; The avoidance cylinder includes an avoidance cylinder barrel, an avoidance piston is provided inside the avoidance cylinder barrel, the avoidance piston is connected to an avoidance piston rod, and an avoidance front end cover and an avoidance rear end cover are respectively connected to both ends of the avoidance cylinder barrel. The avoidance front end cover is provided with a first avoidance oil port, and the avoidance rear end cover is provided with a second avoidance oil port. The first avoidance oil port is connected to the rod chamber of the avoidance cylinder, and the second avoidance oil port is connected to the rodless chamber of the avoidance cylinder. The rodless chamber of the avoidance cylinder is located at the lower part of the rod chamber of the avoidance cylinder. The direction of extension of the avoidance piston rod is opposite to that of extension of the vibration piston rod. After the first avoidance oil port and the second avoidance oil port of the two ice-breaking composite oil cylinders are connected, they are connected to the oil supply port of the constant pressure oil source through a connecting pipe.
[0007] In a preferred embodiment of the present invention, the avoidance piston rod extends or retracts from the middle of the avoidance front end cover, and the vibration piston rod extends or retracts from the middle of the vibration front end cover; the avoidance rear end cover and the vibration rear end cover share a common rear end cover.
[0008] In a preferred embodiment of the present invention, the central axis of the avoidance cylinder and the central axis of the vibration cylinder are arranged coaxially.
[0009] In a preferred embodiment of the present invention, the avoidance front cover and the avoidance rear cover are provided with avoidance dampers, and the vibration front cover and the vibration rear cover are provided with vibration dampers.
[0010] In a preferred embodiment of this utility model, the neutral position of the electro-hydraulic proportional directional valve adopts a Y-type function.
[0011] The beneficial effects of this utility model are as follows: This utility model adopts vibration impact de-icing instead of traditional crushing ice breaking, which does not require a heavy equipment weight. The weight is usually only a fraction of that of traditional ice breaking equipment, which can greatly improve the flexibility of equipment operation and relocation; the vibration impact energy is concentrated, making it easier to break the hard ice layer on the road surface, reducing the energy consumption of the equipment while improving the ice breaking efficiency; the two ice breaking composite cylinders alternately impact the road surface, which can not only reduce the impact on the reaction force of the equipment itself, but also better exert the effect of vibration ice breaking. Attached Figure Description
[0012] Figure 1 This is a schematic diagram of the electro-hydraulic control system of this utility model (the proportional valve core is in the neutral position). Figure 2 This is a schematic diagram of the electro-hydraulic control system of this utility model (the proportional valve core is in the left position). Figure 3 This is a schematic diagram of the electro-hydraulic control system of this utility model (the proportional valve core is in the right position). Figure 4This is a schematic diagram of the internal structure of the ice-breaking composite hydraulic cylinder of this utility model; Figure 5 This is a schematic diagram of the external shape of the ice-breaking composite hydraulic cylinder of this utility model; In the diagram: Avoidance cylinder 1; Avoidance cylinder barrel 101; Avoidance piston 102; Avoidance piston rod 103; First avoidance oil port 104; Second avoidance oil port 105; Avoidance front end cover 106; Common rear end cover 107; Avoidance damper 108; Vibration cylinder 2; Vibration cylinder barrel 201; Vibration piston 202; Vibration piston rod 203; First vibration oil port 204; Second vibration oil port 205; Vibration front end cover 206; Vibration damper 207; Return oil port of constant pressure oil source 3; Supply oil port of constant pressure oil source 4; Electro-hydraulic proportional directional valve 5. Detailed Implementation
[0013] The embodiments of this utility model are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this utility model, and should not be construed as limiting this utility model.
[0014] In the description of this utility model, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," and "counterclockwise," etc., indicating the orientation or positional relationship, are based on the orientation or positional relationship shown in the accompanying drawings and are only for the convenience of describing this utility model and simplifying the description. They do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more of the stated features. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.
[0015] like Figures 1 to 5 The diagram shows a dual-composite hydraulic cylinder alternating impact ice-breaking electro-hydraulic control system, including a return port 3 of a constant pressure oil source, a supply port 4 of a constant pressure oil source, an electro-hydraulic proportional directional valve 5, and two ice-breaking composite hydraulic cylinders; each of the ice-breaking composite hydraulic cylinders includes a vibration cylinder 2, and the vibration cylinders 2 are all single-rod cylinders. The vibrating cylinder 2 includes a vibrating cylinder barrel 201, inside which a vibrating piston 202 is provided. The vibrating piston 202 is connected to a vibrating piston rod 203. The two ends of the vibrating cylinder barrel 201 are respectively connected to a front vibrating cover 206 and a rear vibrating cover. The front vibrating cover 206 is provided with a first vibrating oil port 204, and the rear vibrating cover is provided with a second vibrating oil port 205. The first vibrating oil port 204 is connected to the rod chamber of the vibrating cylinder, and the second vibrating oil port 205 is connected to the rodless chamber of the vibrating cylinder. The rodless chamber of the vibrating cylinder 2 is located above the rod chamber of the vibrating cylinder. like Figures 1 to 3 As shown, the constant pressure oil source supply port 4 in this application is a high-pressure oil circuit. The first vibration oil port 204 of the two ice-breaking composite cylinders are respectively connected to the constant pressure oil source supply port 4, i.e., the high-pressure oil circuit. The second vibration oil port 205 of the two ice-breaking composite cylinders are respectively connected to the two control oil ports of the same electro-hydraulic proportional directional valve 5. The oil supply port and oil return port of the electro-hydraulic proportional directional valve 5 are respectively connected to the constant pressure oil source supply port 4 and the constant pressure oil source return port 3.
[0016] The control system of this application also includes an avoidance cylinder 1 disposed on the upper part of the vibration cylinder 2; The avoidance cylinder 1 includes an avoidance cylinder barrel 101, an avoidance piston 102 is provided inside the avoidance cylinder barrel 101, the avoidance piston 102 is connected to an avoidance piston rod 103, and the two ends of the avoidance cylinder barrel are respectively connected to an avoidance front end cover 106 and an avoidance rear end cover. The avoidance front end cover 106 is provided with a first avoidance oil port 104, and the avoidance rear end cover is provided with a second avoidance oil port 105. The first avoidance oil port 104 is connected to the rod chamber of the avoidance cylinder, and the second avoidance oil port 105 is connected to the rodless chamber of the avoidance cylinder. The rodless chamber of the avoidance cylinder 1 is located at the lower part of the rod chamber of the avoidance cylinder 1. The extension direction of the avoidance piston rod 103 is opposite to that of the vibration piston rod 203. The first avoidance oil port 104, the second avoidance oil port 105 and the first vibration oil port 204 of the two ice-breaking composite oil cylinders are connected to the oil supply port 4 of the constant pressure oil source through connecting pipes, i.e., the high pressure oil circuit.
[0017] The two ice-breaking composite cylinders are located on the left and right sides respectively. The one on the left is the left ice-breaking composite cylinder.
[0018] When the control system of this utility model is working, the constant pressure oil source supplies oil, and the system pressure increases. Since the first avoidance oil port 104 and the second avoidance oil port 105 of the two ice-breaking composite cylinders are connected and connected to the oil supply port 4 of the constant pressure oil source through a connecting pipe, both the rod chamber and the rodless chamber of the avoidance cylinder are under high pressure. However, since the area of the rodless chamber of the avoidance cylinder is larger than the area of the rod chamber, the avoidance piston rod 103 extends. When the ice-breaking device encounters an obstacle, the avoidance piston rod 103 is subjected to external force. When the external force exceeds the hydraulic extension force value set by the avoidance cylinder, the avoidance piston rod 103 retracts under the action of the external force to realize the avoidance action. After the obstacle is passed, the external force disappears or decreases, and the avoidance piston rod 103 resumes extension.
[0019] The system operates in three states: 1. When the electro-hydraulic proportional directional valve signal is zero and the valve core is in the neutral position; 2. When the electro-hydraulic proportional valve core is in the left position; 3. When the electro-hydraulic proportional valve core is in the right position. The operation process of each component in each of the three states will be described below.
[0020] I. State when the electro-hydraulic proportional directional valve signal is zero: The vibrating cylinder in the two ice-breaking composite cylinders has a rod chamber connected to the oil supply port 4 of the constant pressure oil source, and the rod chamber is under high pressure. The rodless chamber is connected to the return port 3 of the constant pressure oil source through the neutral position of the electro-hydraulic proportional valve, and the rodless chamber is under low pressure. The vibrating piston rod 203 retracts.
[0021] II. The state of the electro-hydraulic proportional valve spool when it is in the left position: When the electro-hydraulic proportional directional valve is given a control signal and the valve core is in the left position, the rodless chamber of the vibrating cylinder of the left ice-breaking composite cylinder remains connected to the return port 3 of the constant pressure oil source, maintaining low pressure, and the left vibrating piston rod retracts; the rodless chamber of the vibrating cylinder of the right ice-breaking composite cylinder is connected to the supply port 4 of the constant pressure oil source through the electro-hydraulic proportional valve, the rodless chamber of the vibrating cylinder of the right ice-breaking composite cylinder is under high pressure, and the vibrating piston rod 203 of the right ice-breaking composite cylinder extends.
[0022] III. Constant pressure oil supply, the state of the electro-hydraulic proportional valve core when it is in the right position: When a control signal is applied to the electro-hydraulic proportional directional valve and the valve core is in the right position, the rodless chamber of the vibrating cylinder of the left ice-breaking composite cylinder is connected to the oil supply port 4 of the constant pressure oil source through the electro-hydraulic proportional directional valve. The rodless chamber of the vibrating cylinder of the left ice-breaking composite cylinder is under high pressure, and the vibrating piston rod of the left ice-breaking composite cylinder extends. The rodless chamber of the vibrating cylinder of the right ice-breaking composite cylinder is connected to the oil return port 3 of the constant pressure oil source through the electro-hydraulic proportional valve. The pressure decreases, and the vibrating piston rod of the right ice-breaking composite cylinder retracts. When the control signal of the electro-hydraulic proportional valve changes and the valve core position of the electro-hydraulic proportional valve changes continuously, the vibration cylinders of the two ice-breaking composite cylinders will continuously extend and retract alternately, and the movement directions of the two vibration cylinders are always opposite.
[0023] In a preferred embodiment, the avoidance piston rod 103 extends or retracts from the middle of the avoidance front end cover 106; the vibration piston rod 203 extends or retracts from the middle of the vibration front end cover 206; the avoidance cylinder connection end and the vibration cylinder connection end share a common rear end cover 107, which is convenient to use. The central axis of the avoidance cylinder 1 and the central axis of the vibration cylinder 2 are coaxial.
[0024] The avoidance front cover 106 and the avoidance rear cover are provided with avoidance dampers 108, and the vibration front cover 206 and the vibration rear cover are provided with vibration dampers 207, allowing the hydraulic cylinder to be repeatedly impacted for a long time and at a high frequency.
[0025] The ice-breaking composite hydraulic cylinder of this application consists of two single-rod hydraulic cylinders, which are compact in structure and easy to use; moreover, the single-rod hydraulic cylinders facilitate differential control. During operation, the rod chamber of the cylinder remains connected to the high-pressure oil circuit of the system. By controlling the oil pressure in the rodless chamber, the piston rod of the cylinder can extend or retract. One electro-hydraulic proportional directional valve controls two ice-breaking composite cylinders simultaneously, resulting in a simple hydraulic system and low manufacturing cost. Because the output pressure and direction of the two control ports of the electro-hydraulic proportional directional valve are always opposite, it ensures that when one ice-breaking composite cylinder is rising (retracting), the other is falling (extending), and the two cylinders move alternately. The neutral position of the electro-hydraulic proportional directional valve adopts a Y-type function. When vibration ice breaking is not desired, simply return the electrical control signal of the electro-hydraulic proportional directional valve to zero, and the valve will return to the neutral position. The two controlled ice-breaking composite cylinders will retract simultaneously (with the same stroke), and the ice-breaking device can return to the traditional vibration-free, crushing ice-breaking state. The electro-hydraulic proportional directional valve is controlled by an electrical signal, allowing for easy changes to parameters such as control direction, opening size (corresponding to control flow rate), and reversing frequency, thus achieving programmed control of vibration and impact frequency and impact energy.
[0026] This invention employs vibration impact de-icing instead of traditional crushing ice, thus reducing the equipment's weight. Typically, its weight is only a fraction of that of traditional ice-breaking equipment, significantly improving the flexibility of operation and relocation. The concentrated vibration impact energy more easily breaks down hard ice layers, reducing energy consumption while increasing ice-breaking efficiency. The alternating impact of two composite ice-breaking cylinders not only reduces the impact's reaction force on the equipment itself but also enhances the effectiveness of vibration ice-breaking.
[0027] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of this utility model. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.
[0028] In summary, although the present invention has been disclosed above with reference to preferred embodiments, the above preferred embodiments are not intended to limit the present invention. Those skilled in the art can make various modifications and refinements without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be determined by the scope defined in the claims.
Claims
1. A dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system, characterized in that, It includes a constant pressure oil source, an electro-hydraulic proportional directional valve (5) and two ice-breaking composite cylinders; each of the ice-breaking composite cylinders includes a vibration cylinder (2), and the vibration cylinders (2) are all single-rod cylinders; The vibrating cylinder (2) includes a vibrating cylinder barrel (201), a vibrating piston (202) is provided inside the vibrating cylinder barrel (201), the vibrating piston (202) is connected to a vibrating piston rod (203), the two ends of the vibrating cylinder barrel (201) are respectively connected to a vibrating front end cover (206) and a vibrating rear end cover, the vibrating front end cover (206) is provided with a first vibrating oil port (204), and the vibrating rear end cover is provided with a second vibrating oil port (205); the first vibrating oil port (204) is connected to the rod chamber of the vibrating cylinder, and the second vibrating oil port (205) is connected to the rodless chamber of the vibrating cylinder; the rodless chamber of the vibrating cylinder (2) is located at the upper part of the rod chamber of the vibrating cylinder; The first vibration port (204) of the two ice-breaking composite cylinders is connected to the oil supply port (4) of the constant pressure oil source, and the second vibration port (205) of the two ice-breaking composite cylinders is connected to the two control ports of the same electro-hydraulic proportional directional valve (5). The oil supply port and return port of the electro-hydraulic proportional directional valve (5) are connected to the oil supply port (4) and the return port (3) of the constant pressure oil source, respectively.
2. The dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system according to claim 1, characterized in that, It also includes an avoidance cylinder (1) located on the upper part of the vibration cylinder (2); The avoidance cylinder (1) includes an avoidance cylinder barrel (101), an avoidance piston (102) is provided inside the avoidance cylinder barrel (101), the avoidance piston (102) is connected to an avoidance piston rod (103), the two ends of the avoidance cylinder barrel (101) are respectively connected to an avoidance front end cover (106) and an avoidance rear end cover, the avoidance front end cover (106) is provided with a first avoidance oil port (104), the avoidance rear end cover is provided with a second avoidance oil port (105), the first avoidance oil port (104) is connected to the rod chamber of the avoidance cylinder, and the second avoidance oil port (105) is connected to the rodless chamber of the avoidance cylinder; the rodless chamber of the avoidance cylinder (1) is located at the lower part of the rod chamber of the avoidance cylinder (1); The direction of extension of the avoidance piston rod (103) is opposite to that of extension of the vibration piston rod (203). The first avoidance oil port (104), the second avoidance oil port (105) and the first vibration oil port (204) of the two ice-breaking composite oil cylinders are connected to the oil supply port (4) of the constant pressure oil source through connecting pipes.
3. The dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system according to claim 2, characterized in that, The avoidance piston rod (103) extends or retracts from the middle of the avoidance front end cover (106), and the vibration piston rod (203) extends or retracts from the middle of the vibration front end cover (206); the avoidance rear end cover and the vibration rear end cover share a common rear end cover (107).
4. The dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system according to claim 2, characterized in that, The central axis of the avoidance cylinder (1) and the central axis of the vibration cylinder (2) are arranged coaxially.
5. The dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system according to claim 3, characterized in that, The avoidance front cover (106) and the avoidance rear cover are provided with avoidance dampers (108), and the vibration front cover (206) and the vibration rear cover are provided with vibration dampers (207).
6. The dual-composite-cylinder alternating impact ice-breaking electro-hydraulic control system according to claim 1, characterized in that, The electro-hydraulic proportional directional valve (5) adopts a Y-type function in the middle position.