Paver vibrating hydraulic system, paver and paver vibrating control method

Abstract

The present invention belongs to the technical field of engineering machinery, and specifically relates to a paver vibrating hydraulic system, a paver and a paver vibrating control method. The paver vibrating hydraulic system includes: a hydraulic pump assembly, including a main hydraulic pump with a swash plate, the main hydraulic pump is connected to the engine by transmission; a vibrating motor assembly, the vibrating motor assembly is connected to the main hydraulic pump through a pipeline to form a hydraulic circuit; an adjustment assembly, connected to the pipeline between the main hydraulic pump and the vibrating motor assembly through a pipeline, the adjustment assembly is provided with an adjustment mechanism connected to the swash plate of the main hydraulic pump by transmission; a controller, suitable for adjusting the swash plate angle according to the vibration frequency, the swash plate angle and the speed control of each gear of the engine. Through the technical solution of the present invention, the adjustment method and control logic of the vibration frequency are optimized, the system has high working efficiency, can reduce the influence of the engine gear switching on the vibration frequency, and realize adaptive adjustment, with higher accuracy, which is conducive to improving the quality and efficiency of the vibration operation.

Description

Technical Field

[0001] The invention belongs to the technical field of engineering machinery, and in particular relates to a paver vibrating hydraulic system, a paver and a paver vibrating control method. Background Art

[0002] A vibrating mechanism is usually provided in a paver, and the vibrating mechanism is driven by a hydraulic system to vibrate the road paving materials. The target vibration frequency varies according to different operation requirements. Existing pavers usually use a hydraulic system of a valve-controlled motor or a pump-controlled motor driven by an engine, which does not take into account the change in the corresponding relationship between the engine speed and the flow rate of the hydraulic pump under different gears. It is an open-loop control. When the engine switches gears, the flow rate of the hydraulic pump changes accordingly, causing the vibration frequency to deviate from the target vibration frequency after the gear switch, affecting the quality and efficiency of the vibration operation. Summary of the invention

[0003] In view of this, in order to improve at least one of the above-mentioned problems existing in the prior art, the present invention provides a paver vibrating hydraulic system, a paver and a paver vibrating control method.

[0004] A first aspect of the present invention provides a paver vibrating hydraulic system, comprising: a hydraulic pump assembly, comprising a main hydraulic pump with a swash plate, the main hydraulic pump being transmission-connected to an engine; a vibrating motor assembly, suitable for driving a vibrating mechanism of the paver, the vibrating motor assembly being connected to the main hydraulic pump via a pipeline to form a hydraulic circuit; an adjusting assembly, connected to a pipeline between the main hydraulic pump and the vibrating motor assembly via a pipeline, the adjusting assembly being provided with an adjusting mechanism transmission-connected to the swash plate of the main hydraulic pump, the adjusting mechanism being suitable for driving the swash plate to swing so as to adjust the displacement of the main hydraulic pump; a controller, being communication-connected to the main hydraulic pump and the adjusting assembly, and being suitable for controlling the adjusting assembly to adjust the swash plate angle of the main hydraulic pump according to the correspondence between the vibration frequency, the swash plate angle and the rotational speed of each gear of the engine.

[0005] The beneficial effects of the above technical solution of the present invention are embodied in:

[0006] The displacement adjustment method of the main hydraulic pump has been improved to improve the system working efficiency; at the same time, the displacement adjustment control logic of the main hydraulic pump has been optimized, and the displacement of the main hydraulic pump can be adjusted according to the correspondence between the engine speed in different gears and the swash plate angle of the main hydraulic pump, as well as the correspondence between the swash plate angle and the vibration frequency, so as to keep the flow of the main hydraulic pump constant after the engine switches gears, and then keep the vibration frequency of the vibrating mechanism at the target vibration frequency, which is more in line with actual usage and has higher accuracy. It can be applied to pavers with multiple gears, which is beneficial to improving the quality and efficiency of vibration operations.

[0007] In a feasible implementation, the pipeline connecting the main hydraulic pump and the vibrating motor assembly includes a first main path and a second main path; the main hydraulic pump is a plunger pump provided with an oil drain port and two pumping oil ports, the oil drain port of the main hydraulic pump is connected to the oil tank, an angle sensor is provided on the swash plate of the main hydraulic pump, and the angle sensor is communicatively connected to the controller; the vibrating motor assembly includes a hydraulic motor with two motor oil ports, the output end of the hydraulic motor is suitable for transmission connection with the vibrating mechanism of the paver, one motor oil port of the hydraulic motor is connected to a pumping oil port of the main hydraulic pump through the first main path, and the other motor oil port of the hydraulic motor is connected to another pumping oil port of the main hydraulic pump through the second main path.

[0008] In a feasible implementation, the adjustment component includes: an electric proportional servo valve, which is respectively connected to the first main circuit and the second main circuit through pipelines and is communicatively connected to the controller; an adjustment mechanism, including an adjusting cylinder, which is transmission-connected to the valve core of the electric proportional servo valve and the swash plate of the main hydraulic pump, and the adjusting cylinder is suitable for performing telescopic movement driven by the valve core of the electric proportional servo valve to adjust the swash plate angle of the main hydraulic pump.

[0009] In a feasible implementation, the adjustment component also includes: a first one-way overflow valve, which is arranged in the pipeline connecting the electric proportional servo valve to the first main circuit, and the overflow oil inlet of the first one-way overflow valve is connected to the first main circuit; a second one-way overflow valve, which is arranged in the pipeline connecting the electric proportional servo valve to the second main circuit, and the overflow oil inlet of the second one-way overflow valve is connected to the second main circuit; wherein, the one-way conduction direction of the first one-way overflow valve and the second one-way overflow valve are both from their respective overflow oil outlets to the overflow oil inlet, and the overflow oil outlet of the second one-way overflow valve is connected to the overflow oil outlet of the first one-way overflow valve through a pipeline, and is connected to the electric proportional servo valve through a common pipeline.

[0010] In a feasible implementation, the electric proportional servo valve is provided with a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port is connected to the oil tank through a pipeline, and the second valve port is connected to a common pipeline;

[0011] The adjustment component also includes: a first pressure cut-off valve, the oil inlet of the first pressure cut-off valve is connected to the first main circuit through a pipeline, and the oil outlet of the first pressure cut-off valve is connected to the third valve port of the electric proportional servo valve and the rod chamber of the regulating cylinder through a pipeline; a second pressure cut-off valve, the oil inlet of the second pressure cut-off valve is connected to the second main circuit through a pipeline, and the oil outlet of the second pressure cut-off valve is connected to the fourth valve port of the electric proportional servo valve and the rodless chamber of the regulating cylinder through a pipeline; wherein, the pressure thresholds of the first pressure cut-off valve and the second pressure cut-off valve are both greater than the pressure thresholds of the first one-way relief valve and the second one-way relief valve.

[0012] In a feasible implementation, the hydraulic pump assembly further includes: an oil replenishment pump, which is transmission-connected to the main hydraulic pump, and an oil inlet of the oil replenishment pump is connected to the oil tank;

[0013] The adjustment component also includes: a high-pressure filter, the oil inlet of the high-pressure filter is connected to the oil outlet of the oil replenishment pump through a pipeline, and the oil outlet of the high-pressure filter is connected to the common pipeline through the pipeline; a third overflow valve, the oil inlet of the third overflow valve is connected to the common pipeline through a pipeline, and the oil outlet of the third overflow valve is connected to the oil tank through the pipeline; wherein, the main hydraulic pump, the oil replenishment pump, the electric proportional servo valve, the first one-way overflow valve, the second one-way overflow valve, the third overflow valve, the first pressure cut-off valve, and the second pressure cut-off valve are arranged in an integrated pump body.

[0014] In a feasible implementation, the vibrating motor assembly also includes: a fourth overflow valve, the oil outlet of the fourth overflow valve is connected to the oil tank through a pipeline; a reversing valve, different valve ports on the reversing valve are respectively connected to the first main circuit, the second main circuit and the oil inlet of the fourth overflow valve through pipelines, and the reversing valve is suitable for controlling the oil inlet of the fourth overflow valve to be connected to the first main circuit or the second main circuit, or controlling the oil inlet of the fourth overflow valve to be closed; wherein, the hydraulic motor, the fourth overflow valve and the reversing valve are arranged in an integrated body.

[0015] The second aspect of the present invention further provides a paver, comprising: a vehicle body, on which an engine is provided; a vibrating mechanism connected to the vehicle body; and a paver vibrating hydraulic system according to any one of the above-mentioned first aspects, which is provided on the vehicle body.

[0016] The third aspect of the present invention further provides a paver vibration control method, which is used in the paver vibration hydraulic system of any one of the first aspects or the paver of any one of the second aspects. The paver vibration control method comprises:

[0017] Step S100: obtaining a target vibration frequency of a vibration mechanism of a paver;

[0018] Step S200: acquiring engine status information of the paver and the current swash plate angle of the main hydraulic pump;

[0019] Step S300: determining a target swash plate angle according to a target vibration frequency and engine status information;

[0020] Step S400: adjusting the swash plate angle of the main hydraulic pump according to the current swash plate angle and the target swash plate angle;

[0021] The engine status information includes the gear information and speed information of the engine.

[0022] In a feasible implementation, a controller of the paver vibrating hydraulic system stores a first corresponding relationship curve between the vibration frequency of the vibrating mechanism and the flow rate of the main hydraulic pump, and a second corresponding relationship curve between the engine speed at each gear and the swash plate angle and flow rate of the main hydraulic pump;

[0023] Step S300 of the paver vibration control method: determining a target swash plate angle according to a target vibration frequency and engine status information, including:

[0024] Step S310: determining a target flow rate of the main hydraulic pump according to the target vibration frequency and the first corresponding relationship curve;

[0025] Step S320: determining the current gear and current speed of the engine according to the engine state information;

[0026] Step S330: Determine the target swash plate angle corresponding to the target flow rate according to the current gear position and current speed of the engine and the second corresponding relationship curve.

[0027] In a feasible implementation, step S400 of the paver vibration control method: adjusting the swash plate angle of the main hydraulic pump according to the current swash plate angle and the target swash plate angle includes:

[0028] Step S420: determining whether the current swash plate angle is greater than a first angle threshold, and generating a first determination result;

[0029] If the first judgment result is yes, execute step S430: reduce the swash plate angle of the main hydraulic pump to within the target angle range;

[0030] If the first judgment result is no, executing step S440: judging whether the current swash plate angle is less than a second angle threshold, and generating a second judgment result;

[0031] If the second judgment result is yes, execute step S450: increase the swash plate angle of the main hydraulic pump to within the target angle range;

[0032] If the second judgment result is no, executing step S460: controlling the swash plate angle of the main hydraulic pump to maintain the current swash plate angle;

[0033] The target angle range is [second angle threshold, first angle threshold], the first angle threshold=target swash plate angle+allowable error value, and the second angle threshold=target swash plate angle-allowable error value.

[0034] The fourth aspect of the present invention also provides an electronic device, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein when the processor executes the computer program, a paver vibration control method as described in any one of the third aspects above is implemented.

[0035] The fifth aspect of the present invention further provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the paver vibration control method as described in any one of the third aspects above. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] Figure 1 Shown is a schematic diagram of a paver vibrating hydraulic system provided by an embodiment of the present invention.

[0037] Figure 2 Shown is a schematic diagram of a paver vibrating hydraulic system provided by an embodiment of the present invention.

[0038] Figure 3 Shown is a schematic diagram of a paver vibrating hydraulic system provided by an embodiment of the present invention.

[0039] Figure 4 Shown is a schematic block diagram of a paving machine provided by an embodiment of the present invention.

[0040] Figure 5 The figure is a schematic flow chart of a paver vibration control method provided by an embodiment of the present invention.

[0041] Figure 6 The figure is a schematic flow chart of a paver vibration control method provided by an embodiment of the present invention.

[0042] Figure 7 The figure is a schematic flow chart of a paver vibration control method provided by an embodiment of the present invention.

[0043] Description of reference numerals:

[0044] 1. Hydraulic system of paver vibrator, 10. Integrated hydraulic pump body, 11. Hydraulic pump assembly, 110. Oil tank, 111. Main hydraulic pump, 1111. Swash plate, 1112. Angle sensor, 112. Make-up oil pump, 12. Vibrator motor assembly, 121. Hydraulic motor, 122. Fourth relief valve, 123. Reversing valve, 124. Integrated motor, 13. Adjustment assembly, 131. Electric proportional servo valve, 1311. First valve port, 1312. Second valve port, 1313. Third valve port, 1314. Fourth valve port, 132. Adjustment mechanism, 1321. Adjustment cylinder, 133. First one-way relief valve, 134. Second one-way relief valve, 135. Third relief valve, 136. High-pressure filter, 137. First pressure cut-off valve, 138. Second pressure cut-off valve, 14. Controller, 151. First main road, 152. Second main road, 153. Public pipeline, 2. Paver, 21. Vehicle body, 212. Engine, 22. Vibrator mechanism. DETAILED DESCRIPTION

[0045] In the description of the application, the meaning of "multiple" is at least two, for example, two, three, etc., unless otherwise clearly and specifically limited. In the embodiment of the present application, all directional indications (such as up, down, left, right, front, back, top, bottom ...) are only used to explain the relative position relationship, motion conditions, etc. between the components under a certain specific posture (as shown in the drawings). If the specific posture changes, the directional indication also changes accordingly. In addition, the terms "including" and "having" and any of their deformations are intended to cover non-exclusive inclusions. For example, the process, method, system, product or equipment comprising a series of steps or units are not limited to the steps or units listed, but optionally also include the steps or units not listed, or optionally also include other steps or units inherent to these processes, methods, products or equipment.

[0046] In addition, reference to "embodiments" herein means that a particular feature, structure, or characteristic described in conjunction with the embodiments may be included in at least one embodiment of the present application. The appearance of the phrase in various locations in the specification does not necessarily refer to the same embodiment, nor is it an independent or alternative embodiment that is mutually exclusive with other embodiments. It is explicitly and implicitly understood by those skilled in the art that the embodiments described herein may be combined with other embodiments.

[0047] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0048] Provided below are some embodiments of the paver vibrating hydraulic system, paver and paver vibrating control method in the technical solution of the present invention.

[0049] In an embodiment of the first aspect of the present invention, a paver vibrating hydraulic system 1 is provided. Figure 1 As shown, the paver vibrating hydraulic system 1 includes a hydraulic pump assembly 11 , a vibrating motor assembly 12 , an adjustment assembly 13 and a controller 14 .

[0050] like Figure 1 As shown, the hydraulic pump assembly 11 includes a main hydraulic pump 111 with a swash plate 1111. When applied to a paving machine, the main hydraulic pump 111 is transmission-connected to an engine 212 to obtain power from the engine 212 to drive the hydraulic pump to work.

[0051] like Figure 1As shown, the vibrating motor assembly 12 is connected to the main hydraulic pump 111 through a pipeline to form a hydraulic circuit, so that the oil in the hydraulic circuit is driven to circulate through the main hydraulic pump 111, and high-pressure oil is supplied to the vibrating motor assembly 12 to drive the vibrating motor assembly 12 to work. The vibrating motor assembly 12 can be connected to the vibrating mechanism of the paver to drive the vibrating mechanism to perform a vibrating operation. Among them, the oil in the vibrating motor assembly 12 can also flow back to the main hydraulic pump 111 to achieve a circulating flow.

[0052] like Figure 1 As shown, the adjustment component 13 is connected to the pipeline between the main hydraulic pump 111 and the vibrating motor assembly 12 through a pipeline, and the adjustment component 13 is provided with an adjustment mechanism 132, and the adjustment mechanism 132 is transmission-connected to the swash plate 1111 of the main hydraulic pump 111 to drive the swash plate 1111 to swing, change the swash plate angle of the main hydraulic pump 111, thereby adjusting the displacement of the main hydraulic pump 111, and further changing the flow rate of the main hydraulic pump 111. The controller 14 is in communication connection with the adjustment component 13. The controller 14 can determine the target swash plate angle corresponding to the target vibration frequency according to the corresponding relationship between the vibration frequency of the vibration mechanism, the swash plate angle of the main hydraulic pump 111, and the speed of each gear of the engine 212, and send a corresponding control instruction to the adjustment component 13, so that the adjustment component 13 performs a corresponding adjustment operation, and uses the regulating mechanism 132 to adjust the swash plate angle of the main hydraulic pump 111 to the target swash plate angle, so that the displacement of the main hydraulic pump 111 matches the speed of the engine 212 in the current gear, so that the flow of the main hydraulic pump 111 remains constant, and the gear switching of the engine 212 is prevented from affecting the vibration frequency of the vibration mechanism. When the vibration frequency changes, the controller 14 can perform a corresponding adjustment control operation on the swash plate angle of the main hydraulic pump 111 to achieve angle closed-loop control.

[0053] It can be understood that the main hydraulic pump 111 supplies oil to the vibrating motor assembly 12, so there is a corresponding relationship between the vibration frequency of the vibrating mechanism and the flow of the main hydraulic pump 111. Specifically, the vibration frequency of the vibrating mechanism = (flow of the main hydraulic pump / displacement of the hydraulic motor) / 60, where the displacement of the hydraulic motor is usually a fixed value; and there is a corresponding relationship between the flow of the main hydraulic pump 111 and the displacement (related to the swash plate angle) and the speed of the engine 212. Specifically, the flow of the main hydraulic pump = displacement of the main hydraulic pump × the speed of the engine, where the speed of the engine 212 is different in different gears, and the corresponding flow of the main hydraulic pump 111 is different, that is, the corresponding relationship between different gears of the engine and the vibration frequency is different, so the gear of the engine 212 will also affect the vibration frequency of the vibrating mechanism. In the hydraulic system of the vibrating mechanism of the existing paver, the same speed-swash plate angle-flow correspondence curve is usually used, and the hydraulic system is generally open-loop control. The gear change of the engine 212 will affect the vibration frequency. For example, when the gear of the engine 212 is switched from a high-speed gear to a low-speed gear, the actual vibration frequency has changed, and the speed drop phenomenon is likely to occur during the operation. When the gear of the engine 212 is switched from a low-speed gear to a high-speed gear, the vibration frequency will increase again. That is, the gear change of the engine 212 causes the vibration frequency to deviate from the target vibration frequency, affecting the quality and efficiency of the construction operation.

[0054] The paver vibrating hydraulic system 1 in this embodiment adjusts the swash plate angle of the main hydraulic pump 111 according to the corresponding relationship between the vibration frequency, the swash plate angle and the speed of the engine 212 at different gears. When the engine 212 switches gears, the target swash plate angle corresponding to the target vibration frequency also changes immediately, so that the flow of the main hydraulic pump 111 remains constant, and then the vibration frequency of the vibrating mechanism remains at the target vibration frequency. The control operation is more accurate and more in line with the actual construction conditions of the paver; in addition, by adopting angle closed-loop control, the controller 14 can adjust the swash plate angle of the main hydraulic pump 111 accordingly to prevent the vibration frequency from deviating from the target vibration frequency during the operation, which is conducive to improving the operation quality and efficiency of the paver.

[0055] It should be noted that the gears of the engine 212 described in this embodiment may be two, for example, an economic gear and a rated gear, the economic gear corresponds to a low speed, and the rated gear corresponds to a high speed. Of course, the number of gears may be greater than two. In addition, a target swash plate angle corresponding to the target vibration frequency may be set with an allowable error range. When the swash plate angle of the main hydraulic pump 111 is adjusted to a difference with the target swash plate angle within the error range, it can be considered that the target swash plate angle has been adjusted, and the adjustment control operation is completed.

[0056] In some embodiments of the present invention, Figure 1As shown, in the paver vibrating hydraulic system 1, the pipeline between the main hydraulic pump 111 and the vibrating motor assembly 12 specifically includes a first main path 151 and a second main path 152. The main hydraulic pump 111 is specifically a plunger pump, and the main hydraulic pump 111 is provided with an oil drain port and two pump oil ports, the oil drain port is connected to the oil tank 110, one pump oil port is connected to the first main path 151, and the other pump oil port is connected to the second main path 152. Among them, an angle sensor 1112 for detecting the angle of the swash plate is provided on the swash plate 1111 of the main hydraulic pump 111, and the angle sensor 1112 is connected to the controller 14 for data transmission. Correspondingly, the vibrating motor assembly 12 includes a hydraulic motor 121, and the hydraulic motor 121 is provided with two motor oil ports and an output end. One motor oil port of the hydraulic motor 121 is connected to the first main circuit 151, and the other motor oil port is connected to the second main circuit 152, so as to form a hydraulic circuit between the hydraulic motor 121 and the main hydraulic pump 111 through the first main circuit 151 and the second main circuit 152; the output end of the hydraulic motor 121 is used for transmission connection with the vibrating mechanism to output power to the vibrating mechanism and drive the vibrating mechanism to perform vibrating operation.

[0057] Specifically, when the main hydraulic pump 111 supplies oil to the hydraulic motor 121 through the first main path 151, the hydraulic oil flowing through the hydraulic motor 121 drives the hydraulic motor 121 to work, and then flows back to the main hydraulic pump 111 through the second main path 152; wherein, the first main path 151 is the high-pressure side, and the second main path 152 is the low-pressure side; the situation is similar to this, the first main path 151 is the low-pressure side, and the second main path 152 is the high-pressure side. If the vibration frequency of the vibration mechanism deviates from the target vibration frequency during the operation, it is transmitted to the main hydraulic pump 111 through the first main path 151 and the second main path 152, and the swash plate angle of the main hydraulic pump 111 can be detected by the angle sensor 1112, and the corresponding control operation is performed through the controller 14, so that the vibration frequency of the vibration mechanism is restored to the target vibration frequency, and the angle closed-loop control is realized.

[0058] In some embodiments of the present invention, Figure 1 and Figure 2As shown, in the paver vibrating hydraulic system 1, the adjustment component 13 includes an electric proportional servo valve 131 and an adjustment mechanism 132. The electric proportional servo valve 131 is connected to the controller 14 in communication so as to work according to the control instruction of the controller 14; the electric proportional servo valve 131 is connected to the first main path 151 and the second main path 152 through pipelines. The adjustment mechanism 132 specifically includes an adjustment cylinder 1321, and the adjustment cylinder 1321 is connected to the valve core of the electric proportional servo valve 131 through a mechanical connection, so that when the valve core of the electric proportional servo valve 131 moves, the adjustment cylinder 1321 is driven to perform telescopic movement, thereby driving the swash plate 1111 of the main hydraulic pump 111 to change its angle, thereby realizing the displacement adjustment operation of the main hydraulic pump 111. Among them, the movement of the valve core of the electric proportional servo valve 131 is a continuous progressive movement process, and moves according to the control instruction of the controller 14, thereby driving the swash plate angle of the main hydraulic pump 111 to change, and the accuracy and precision are high.

[0059] In some embodiments of the present invention, Figure 1 and Figure 2 As shown, the adjustment component 13 also includes a first one-way relief valve 133 and a second one-way relief valve 134, which act as high-pressure relief valves in the system. The first one-way relief valve 133 and the second one-way relief valve 134 are both provided with an overflow oil inlet and an overflow oil outlet. When the oil pressure of the overflow oil inlet is greater than a preset pressure threshold, the overflow oil inlet and the overflow oil outlet are connected. In addition, the one-way conduction direction of the first one-way relief valve 133 is from the overflow oil outlet to the overflow oil inlet. Similarly, the one-way conduction direction of the second one-way relief valve 134 is also from the overflow oil outlet to the overflow oil inlet. The first one-way relief valve 133 is arranged in the pipeline connecting the electric proportional servo valve 131 to the first main circuit 151, and the second one-way relief valve 134 is arranged in the pipeline connecting the electric proportional servo valve 131 to the second main circuit 152; wherein, the overflow oil inlet of the first one-way relief valve 133 is connected to the first main circuit 151 through a pipeline, and the overflow oil inlet of the second one-way relief valve 134 is connected to the second main circuit 152 through a pipeline, and the overflow oil outlet of the first one-way relief valve 133 is connected to the overflow oil outlet of the second one-way relief valve 134 through a pipeline, and is connected to the electric proportional servo valve 131 through a common pipeline 153.

[0060] It can be understood that the one-way overflow valve is usually provided with an overflow channel and a one-way channel, such as Figure 1 The first one-way overflow valve 133 and the second one-way overflow valve 134 are shown in the figure, wherein the conduction directions of the overflow channel and the one-way channel are opposite.

[0061] When the oil pressure in the first main path 151 is too high and exceeds the set pressure threshold of the first one-way relief valve 133, the overflow channel of the first one-way relief valve 133 is opened; when the oil pressure in the second main path 152 is too high and exceeds the set pressure threshold of the second one-way relief valve 134, the overflow channel of the second one-way relief valve 134 is opened. Since one of the first main path 151 and the second main path 152 is a high-pressure side and the other is a low-pressure side, part of the oil overflowing through the first one-way relief valve 133 or the second one-way relief valve 134 will flow into the low-pressure side pipeline through the one-way channel of the one-way relief valve connected to the low-pressure side. For example, when the first main path 151 is on the high-pressure side, the second main path 152 is on the low-pressure side. At this time, if the oil pressure in the first main path 151 is greater than the pressure threshold of the first one-way relief valve 133, the overflow channel of the first one-way relief valve 133 is connected, and part of the oil in the first main path 151 overflows through the first one-way relief valve 133 and flows into the second main path 152 through the one-way channel of the second one-way relief valve 134, that is, the high-pressure oil flows from the high-pressure side to the low-pressure side, thereby realizing the overflow protection function. The situation where the second main path 152 is on the high-pressure side is similar to this, and will not be repeated here.

[0062] Furthermore, if Figure 2 As shown, the adjustment component 13 also includes a first pressure cut-off valve 137 and a second pressure cut-off valve 138. The electric proportional servo valve 131 is a valve body with an H-type neutral position function. The electric proportional servo valve 131 is provided with four valve ports: a first valve port 1311, a second valve port 1312, a third valve port 1313 and a fourth valve port 1314; when the electric proportional servo valve 131 is in the neutral position, the four valve ports are mutually connected through the H-type neutral position function, and the oil circuit corresponding to each valve port in the valve core has a damping and throttling effect, which can slow down the flow rate and alleviate the impact. Among them, the first valve port 1311 of the electric proportional servo valve 131 is connected to the oil tank 110 through a pipeline, and the second valve port 1312 is connected to the common pipeline 153. The oil inlet of the first pressure cut-off valve 137 is connected to the first main circuit 151 through a pipeline, and the oil outlet of the first pressure cut-off valve 137 is connected to the third valve port 1313 of the electric proportional servo valve 131 and the rod chamber of the regulating cylinder 1321 through a pipeline; the oil inlet of the second pressure cut-off valve 138 is connected to the second main circuit 152 through a pipeline, and the oil outlet of the second pressure cut-off valve 138 is connected to the fourth valve port 1314 of the electric proportional servo valve 131 and the rodless chamber of the regulating cylinder 1321 through a pipeline.

[0063] Among them, in the non-working state, the electric proportional servo valve 131 is in the middle position. At this time, the rod chamber and the rodless chamber of the adjusting cylinder 1321 are connected to each other through the H-type middle position function, and the oil on the high-pressure side slowly flows into the low-pressure side, so that the piston of the adjusting cylinder 1321 is in a floating state, and the balance is maintained between the rod chamber and the rodless chamber.

[0064] The pressure thresholds of the first pressure cut-off valve 137 and the second pressure cut-off valve 138 are both greater than the pressure thresholds of the first one-way relief valve 133 and the second one-way relief valve 134. Specifically, the pressure thresholds of the first pressure cut-off valve 137 and the second pressure cut-off valve 138 can be set to be 20 bar to 30 bar higher than the pressure thresholds of the first one-way relief valve 133 and the second one-way relief valve 134. When the oil pressure is much greater than the pressure thresholds of the first one-way relief valve 133 and the second one-way relief valve 134, the overflow effect of the first one-way relief valve 133 or the second one-way relief valve 134 cannot meet the overflow unloading requirements. For example, when a continuous high pressure occurs in the hydraulic system and exceeds the set value of the pressure cut-off valve, one of the first pressure cut-off valve 137 or the second pressure cut-off valve 138 corresponding to the high pressure side is turned on, and the oil on the high pressure side flows into the regulating cylinder 1321 through the first pressure cut-off valve 137 or the second pressure cut-off valve 138.

[0065] For example, if the high pressure in the first main circuit 151 continues and exceeds the set value of the first pressure cut-off valve 137, the first pressure cut-off valve 137 is turned on, and the high-pressure oil in the first main circuit 151 flows into the rod chamber of the regulating cylinder 1321 through the first pressure cut-off valve 137, and drives the piston of the regulating cylinder 1321 to contract, driving the swash plate 1111 of the main hydraulic pump 111 to return to the middle position; at this time, the valve core of the electric proportional servo valve 131 is switched to the corresponding position, so that the excess oil in the rodless chamber of the regulating cylinder 1321 can flow back to the oil tank through the electric proportional servo valve 131. If the high pressure in the second main circuit 152 continues and exceeds the set value of the second pressure cut-off valve 138, the second pressure cut-off valve 138 is turned on, and the high-pressure oil in the second main circuit 152 flows into the rodless chamber of the regulating cylinder 1321 through the second pressure cut-off valve 138, and drives the piston of the regulating cylinder 1321 to extend, driving the swash plate 1111 of the main hydraulic pump 111 to return to the middle position; at this time, the valve core of the electric proportional servo valve 131 is switched to the corresponding position, so that the excess oil in the rod chamber of the regulating cylinder 1321 flows back to the oil tank through the electric proportional servo valve 131. It can be understood that when the swash plate 1111 of the main hydraulic pump 111 is in the middle position, the pressure difference between the two pump oil ports is zero, thereby playing a role in pressure cutting, alleviating pressure shock, and also playing a role in safety protection.

[0066] In some embodiments of the present invention, Figure 2As shown, in the paver vibrating hydraulic system 1, the hydraulic pump assembly 11 also includes an oil replenishing pump 112, and the adjustment assembly 13 also includes a high-pressure filter 136 and a third relief valve 135. The oil replenishing pump 112 is connected to the main hydraulic pump 111 by transmission, and operates synchronously with the main hydraulic pump 111; the oil inlet of the oil replenishing pump 112 is connected to the oil tank 110 through a pipeline, and the oil outlet of the oil replenishing pump 112 is connected to the oil inlet of the high-pressure filter 136 through a pipeline, and the oil outlet of the high-pressure filter 136 is connected to the common pipeline 153 through a pipeline. The oil inlet of the third relief valve 135 is connected to the common pipeline 153 through a pipeline, and the oil outlet of the third relief valve 135 is connected to the oil tank 110 through a pipeline, so that the third relief valve 135 and the oil replenishing pump 112 form a parallel relationship, and the third relief valve 135 acts as an oil replenishing relief valve.

[0067] The oil supplied by the replenishing pump 112 is filtered by the high-pressure filter 136 and flows into the common pipeline 153 to replenish the oil leaked during the use of the hydraulic system, so that the total flow of oil in the system can meet the normal use requirements. The third relief valve 135 is used to limit the pressure of the oil replenished by the replenishing pump 112. When the replenished oil is excessive, the third relief valve 135 is turned on to overflow and unload, so as to prevent the replenished oil from affecting the normal pressure in the system.

[0068] In addition, when the first pressure cut-off valve 137 or the second pressure cut-off valve 138 is turned on, while the swash plate 1111 of the main hydraulic pump 111 is driven to return to the middle position by the regulating cylinder 1321, the excess oil can also flow into the common pipeline 153 through the corresponding valve port of the electric proportional servo valve 131. At this time, due to the high oil pressure, the third relief valve 135 is turned on and relief unloading is performed.

[0069] Furthermore, if Figure 3 In the example, the main hydraulic pump 111, the supplementary oil pump 112, the electric proportional servo valve 131, the first one-way relief valve 133, the second one-way relief valve 134, the first pressure cut-off valve 137, and the second pressure cut-off valve 138 are arranged in an integrated pump body to form an integrated hydraulic pump body 10, the first main circuit 151 is connected to one pumping port of the main hydraulic pump 111 through the A port of the integrated hydraulic pump body 10, and the second main circuit 152 is connected to another pumping port of the main hydraulic pump 111 through the B port of the integrated hydraulic pump body 10. Through the above integrated design, the system structure is simplified and easy to assemble in the paver.

[0070] In some embodiments, Figure 3As shown, in the paver vibrating hydraulic system 1, the vibrating motor assembly 12 further includes a fourth overflow valve 122 and a reversing valve 123. The oil outlet of the fourth overflow valve 122 is connected to the oil tank 110 through a pipeline, the oil inlet of the fourth overflow valve 122 is connected to a valve port of the reversing valve 123 through a pipeline, and the other two valve ports of the reversing valve 123 are respectively connected to the two motor oil ports of the hydraulic motor 121. Specifically, as Figure 3 In the example in, the reversing valve 123 can specifically adopt a three-position two-way valve, which changes the connection relationship between the oil inlet of the fourth relief valve 122 and the hydraulic motor 121 by reversing, so that according to the pressure between the two motor oil ports of the hydraulic motor 121, the oil inlet of the fourth relief valve 122 is connected to a motor oil port on the high-pressure side, so that the fourth relief valve 122 acts as a high-pressure relief valve to provide overflow protection for the hydraulic motor 121.

[0071] Furthermore, if Figure 3 As shown in FIG. 1 , the hydraulic motor 121 , the fourth overflow valve 122 and the reversing valve 123 are arranged in the same integrated body to form an integrated motor 124 to simplify the structure and facilitate assembly in the paving machine.

[0072] The following is a specific embodiment of the paver vibrating hydraulic system 1 of the present invention:

[0073] like Figure 3 As shown, the paver vibrating hydraulic system 1 includes a hydraulic pump assembly 11 , a vibrating motor assembly 12 , an adjustment assembly 13 and a controller 14 .

[0074] The hydraulic pump assembly 11 includes a main hydraulic pump 111 with a swash plate 1111 and a supplementary oil pump 112. The main hydraulic pump 111 is specifically a plunger pump, and the main hydraulic pump 111 is provided with an oil drain port and two pumping ports, and the oil drain port is connected to the oil tank 110. Among them, the swash plate 1111 of the main hydraulic pump 111 is provided with an angle sensor 1112 for detecting the angle of the swash plate, and the angle sensor 1112 is communicatively connected with the controller 14. When applied to a paving machine, the main hydraulic pump 111 is transmission-connected to the engine 212 to obtain power through the engine 212 to drive the hydraulic pump to work. The supplementary oil pump 112 is transmission-connected to the main hydraulic pump 111 and operates synchronously with the main hydraulic pump 111; the oil inlet of the supplementary oil pump 112 is connected to the oil tank 110 through a pipeline.

[0075] The vibrating motor assembly 12 includes a hydraulic motor 121, a fourth overflow valve 122 and a reversing valve 123. The hydraulic motor 121 is provided with two motor oil ports and an output end. The output end of the hydraulic motor 121 is used for transmission connection with the vibrating mechanism of the paver to output power to the vibrating mechanism and drive the vibrating mechanism to perform a vibrating operation. The two pump oil ports of the main hydraulic pump 111 correspond to the two motor oil ports of the hydraulic motor 121 one by one, and are connected through the first main path 151 and the second main path 152 respectively. Specifically, one end of the first main circuit 151 is connected to a pumping port of the main hydraulic pump 111, and the other end is connected to a motor oil port of the hydraulic motor 121; one end of the second main circuit 152 is connected to another pumping port of the main hydraulic pump 111, and the other end is connected to another motor oil port of the hydraulic motor 121, so that a hydraulic circuit is formed between the hydraulic motor 121 and the main hydraulic pump 111 through the first main circuit 151 and the second main circuit 152, so that the main hydraulic pump 111 supplies oil to the hydraulic motor 121, drives the hydraulic motor 121 to operate, and then drives the vibration mechanism to perform the vibration operation. When the main hydraulic pump 111 supplies oil to the hydraulic motor 121 through the first main circuit 151, the hydraulic oil flowing through the hydraulic motor 121 drives the hydraulic motor 121 to work, and then flows back to the main hydraulic pump 111 through the second main circuit 152; the situation is similar in reverse. Among them, in the first main path 151 and the second main path 152, the one supplying oil to the hydraulic motor 121 is the high-pressure side, and the one returning oil from the hydraulic motor 121 to the main hydraulic pump 111 is the low-pressure side.

[0076] like Figure 3 In the example in FIG. 1 , the reversing valve 123 can be a three-position two-way valve, and is connected to the two motor oil ports of the hydraulic motor 121 and the oil inlet of the fourth relief valve 122 through pipelines, and the oil outlet of the fourth relief valve 122 is connected to the oil tank 110 through pipelines. The reversing valve 123 can make the oil inlet of the fourth relief valve 122 connected to a motor oil port on the high-pressure side through a reversing operation according to the pressure relationship between the two motor oil ports of the hydraulic motor 121, so that the fourth relief valve 122 acts as a high-pressure relief valve to protect the hydraulic motor 121 from overflow. The hydraulic motor 121, the fourth relief valve 122 and the reversing valve 123 are arranged in the same integrated body to form an integrated motor 124.

[0077] like Figure 3 As shown, the adjustment assembly 13 includes an electric proportional servo valve 131 , an adjusting mechanism 132 , a first one-way relief valve 133 , a second one-way relief valve 134 , a first pressure cut-off valve 137 , a second pressure cut-off valve 138 , a high-pressure filter 136 and a third relief valve 135 .

[0078] The electric proportional servo valve 131 is connected to the controller 14 in communication so as to work according to the control instruction of the controller 14; the electric proportional servo valve 131 is a valve body with an H-type neutral position function, and the electric proportional servo valve 131 is provided with four valve ports: a first valve port 1311, a second valve port 1312, a third valve port 1313 and a fourth valve port 1314; when the electric proportional servo valve 131 is in the neutral position, the four valve ports are mutually connected through the H-type neutral position function, and the oil circuit corresponding to each valve port in the valve core has a throttling effect, which can slow down the flow rate. Among them, the first valve port 1311 of the electric proportional servo valve 131 is connected to the oil tank 110 through a pipeline. The adjusting mechanism 132 specifically includes an adjusting cylinder 1321, which is mechanically connected to the valve core of the electric proportional servo valve 131, so that when the valve core of the electric proportional servo valve 131 moves, the adjusting cylinder 1321 is driven to perform telescopic movement, thereby driving the angle of the swash plate of the main hydraulic pump 111 to change, thereby realizing the displacement adjustment operation of the main hydraulic pump 111.

[0079] The first one-way relief valve 133 and the second one-way relief valve 134 function as high-pressure relief valves, and both the first one-way relief valve 133 and the second one-way relief valve 134 are provided with an overflow oil inlet and an overflow oil outlet, and both are provided with an overflow channel and a one-way channel inside, and the overflow channel and the one-way channel have opposite conduction directions. When the oil pressure of the overflow oil inlet is greater than a preset pressure threshold, the overflow oil inlet is conducted to the overflow oil outlet. The first one-way relief valve 133 is arranged in the pipeline connecting the electric proportional servo valve 131 to the first main circuit 151, and the second one-way relief valve 134 is arranged in the pipeline connecting the electric proportional servo valve 131 to the second main circuit 152; wherein, the overflow oil inlet of the first one-way relief valve 133 is connected to the first main circuit 151 through a pipeline, and the overflow oil inlet of the second one-way relief valve 134 is connected to the second main circuit 152 through a pipeline, and the overflow oil outlet of the first one-way relief valve 133 is connected to the overflow oil outlet of the second one-way relief valve 134 through a pipeline, and is connected to the second valve port 1312 of the electric proportional servo valve 131 through a common pipeline 153.

[0080] For example, when the first main circuit 151 is on the high-pressure side and the second main circuit 152 is on the low-pressure side, if the oil pressure in the first main circuit 151 exceeds the set pressure threshold of the first one-way relief valve 133, the overflow channel of the first one-way relief valve 133 is opened; part of the oil in the first main circuit 151 overflows through the first one-way relief valve 133 and flows out from the overflow oil outlet of the first one-way relief valve 133, and the one-way channel of the second one-way relief valve 134 is opened by pressure, and flows into the second main circuit 152 through the one-way channel of the second one-way relief valve 134, that is, the high-pressure oil flows from the high-pressure side to the low-pressure side, thereby realizing the overflow protection function. The situation where the second main circuit 152 is on the high-pressure side is similar to this, and will not be repeated here.

[0081] like Figure 3 As shown, the oil outlet of the replenishing pump 112 is connected to the oil inlet of the high-pressure filter 136 through a pipeline, and the oil outlet of the high-pressure filter 136 is connected to the common pipeline 153 through a pipeline. The oil inlet of the third relief valve 135 is connected to the common pipeline 153 through a pipeline, and the oil outlet of the third relief valve 135 is connected to the oil tank 110 through a pipeline, so that the third relief valve 135 and the replenishing pump 112 form a parallel relationship, and the third relief valve 135 acts as an oil replenishing relief valve. The oil supplied by the replenishing pump 112 is filtered by the high-pressure filter 136 and flows into the common pipeline 153 to replenish the oil leaked during the use of the hydraulic system, so that the total flow of oil in the system can meet the normal use requirements. The third relief valve 135 is used to limit the pressure of the oil replenished by the replenishing pump 112. When the replenished oil is excessive, the third relief valve 135 is turned on to overflow and unload, so as to prevent the replenished oil from affecting the normal pressure in the system.

[0082] like Figure 3 As shown, the oil inlet of the first pressure cut-off valve 137 is connected to the first main circuit 151 through a pipeline, and the oil outlet of the first pressure cut-off valve 137 is connected to the third valve port 1313 of the electric proportional servo valve 131 and the rod chamber of the regulating oil cylinder 1321 through a pipeline; the oil inlet of the second pressure cut-off valve 138 is connected to the second main circuit 152 through a pipeline, and the oil outlet of the second pressure cut-off valve 138 is connected to the fourth valve port 1314 of the electric proportional servo valve 131 and the rodless chamber of the regulating oil cylinder 1321 through a pipeline. Among them, the pressure thresholds of the first pressure cut-off valve 137 and the second pressure cut-off valve 138 are 20 bar to 30 bar higher than those of the first one-way relief valve 133 and the second one-way relief valve 134.

[0083] When the oil pressure in the system is much greater than the pressure thresholds of the first one-way relief valve 133 and the second one-way relief valve 134, for example, when a continuous high pressure occurs in the hydraulic system and exceeds the set value of the pressure cut-off valve, the overflow effect of the first one-way relief valve 133 or the second one-way relief valve 134 cannot meet the overflow unloading requirements, and one of the first pressure cut-off valve 137 or the second pressure cut-off valve 138 corresponding to the high-pressure side is turned on, and the oil on the high-pressure side flows into the regulating cylinder 1321 through the first pressure cut-off valve 137 or the second pressure cut-off valve 138, and drives the regulating cylinder 1321 to adjust the pressure. The piston of 321 performs corresponding extension or contraction movement, driving the swash plate 1111 of the main hydraulic pump 111 to return to the middle position; at this time, the valve core of the electric proportional servo valve 131 is switched to the corresponding position, and the excess oil flowing through the first pressure cut-off valve 137 or the second pressure cut-off valve 138 enters the common pipeline 153 through the second valve port 1312 of the electric proportional servo valve 131, and conducts the third overflow valve 135 for overflow unloading. At the same time, the excess oil in the rodless chamber or the rod chamber of the regulating cylinder 1321 flows back to the oil tank through the first valve port 1311 of the electric proportional servo valve 131. When the swash plate 1111 of the main hydraulic pump 111 is in the middle position, the pressure difference between the two pump oil ports is zero, thereby playing a role in pressure cut-off, alleviating pressure shock, and also playing a role in safety protection.

[0084] In the non-working state, the electric proportional servo valve 131 is in the middle position. At this time, the rod chamber and the rodless chamber of the regulating cylinder are connected to each other through the H-type middle position function, and the oil on the high-pressure side slowly flows into the low-pressure side to make the piston of the regulating cylinder in a floating state, and maintain balance between the rod chamber and the rodless chamber.

[0085] Among them, Figure 3 In the example, the main hydraulic pump 111, the replenishing oil pump 112, the electric proportional servo valve 131, the first one-way relief valve 133, the second one-way relief valve 134, the first pressure cut-off valve 137, and the second pressure cut-off valve 138 are arranged in an integrated hydraulic pump body 10, which simplifies the system structure and facilitates assembly in the paver.

[0086] The controller 14 can obtain the swash plate angle information of the main hydraulic pump 111 through the angle sensor 1112, and the controller 14 can also communicate with the engine 212 to obtain the gear state of the engine 212. The controller 14 determines the target swash plate angle corresponding to the target vibration frequency according to the corresponding relationship between the vibration frequency of the vibration mechanism, the swash plate angle of the main hydraulic pump 111, and the rotation speed of each gear of the engine 212, and sends a corresponding control instruction to the adjustment component 13, so that the adjustment component 13 performs a corresponding adjustment operation, and uses the adjustment mechanism 132 to adjust the swash plate angle of the main hydraulic pump 111 to the target swash plate angle, so that the flow of the main hydraulic pump 111 remains constant and matches the target vibration frequency of the vibration mechanism, so as to maintain the target vibration frequency required by the vibration operation.

[0087] For example, when the engine 212 is provided with an economic gear and a rated gear, the speed of the rated gear is greater than the speed of the economic gear. Different corresponding relationship curves are formed between the speed of the engine 212 in the economic gear and the rated gear and the swash plate angle and flow rate of the main hydraulic pump 111, while another corresponding relationship curve is formed between the flow rate of the main hydraulic pump 111 and the vibration frequency of the vibration mechanism driven by the hydraulic motor 121. The controller 14 adjusts and controls the swash plate angle of the main hydraulic pump 111 according to the specific gear state of the engine 212 using the corresponding relationship curve under the corresponding gear, so that the flow rate of the main hydraulic pump 111 remains constant, and the vibration frequency of the vibration mechanism remains at the target vibration frequency. Among them, the target swash plate angle corresponding to the target vibration frequency can be set with an allowable error range. When the swash plate angle of the main hydraulic pump 111 is adjusted to a difference with the target swash plate angle within the error range, it can be considered that it has been adjusted to the target swash plate angle, and the adjustment control operation is completed.

[0088] In addition, the oil in the hydraulic motor 121 can also flow back to the main hydraulic pump 111 to achieve circulation. When the vibration frequency changes, the angle sensor 1112 can detect the swash plate angle of the main hydraulic pump 111, and the controller 14 can perform corresponding adjustment and control operations to achieve angle closed-loop control.

[0089] The paver vibrating hydraulic system 1 in this embodiment adjusts the swash plate angle of the main hydraulic pump 111 according to the corresponding relationship among the vibration frequency, the swash plate angle and the rotational speed of the engine 212 in different gears. When the engine 212 switches gears, the target swash plate angle corresponding to the target vibration frequency also changes randomly, and the control operation is more accurate and more in line with the actual construction conditions of the paver. In addition, by adopting angle closed-loop control, corresponding adjustment control operations can be performed according to changes in the vibration frequency to prevent the vibration frequency from deviating from the target vibration frequency during the operation, which is beneficial to improving the operation quality and efficiency of the paver.

[0090] In addition, this embodiment also adopts an integrated design, which simplifies the system structure and facilitates assembly on the paver.

[0091] In an embodiment of the second aspect of the present invention, a paving machine 2 is also provided, such as Figure 1 and Figure 4As shown, the paver 2 includes a vehicle body 21, a vibrating mechanism 22, and a paver vibrating hydraulic system 1 in any embodiment of the first aspect. The vehicle body 21 is provided with an engine 212, which is transmission-connected to the main hydraulic pump 111 of the paver vibrating hydraulic system 1 to provide power to the main hydraulic pump 111. The vibrating mechanism 22 is connected to the vehicle body 21 and is transmission-connected to the vibrating motor assembly 12 of the paver vibrating hydraulic system 1 to perform a vibrating operation under the drive of the vibrating motor assembly 12; at the same time, the vibrating mechanism 22 can move with the travel of the vehicle body 21.

[0092] Furthermore, the engine 212 can also be set with a plurality of different gears, such as an economic gear and a rated gear. The controller 14 of the paver vibrating hydraulic system 1 is connected to the engine 212 in communication to obtain the gear information of the engine 212, and according to different gears, the corresponding corresponding relationship curve is used to adjust the swash plate angle of the main hydraulic pump 111 to adjust the displacement of the main hydraulic pump 111 so that the flow of the main hydraulic pump remains constant, thereby keeping the vibration frequency of the vibrating mechanism 22 at the target vibration frequency to meet the construction work requirements. Among them, the adjustment control operation is more accurate, and the angle closed-loop control is adopted, and the adaptive adjustment operation can also be realized, which is conducive to further improving the operation efficiency and operation quality of the vibrating mechanism 22.

[0093] In addition, the paver 2 in this embodiment also has all the beneficial effects of the paver vibrating hydraulic system 1 in any of the above embodiments, which will not be repeated here.

[0094] In the embodiment of the third aspect of the present invention, a paver vibration control method is also provided, which is applied to the paver vibration hydraulic system in any embodiment of the first aspect or the paver in the embodiment of the second aspect. Figure 5 As shown, the paver vibration control method includes:

[0095] Step S100: obtaining a target vibration frequency of a vibration mechanism of a paver;

[0096] Step S200: obtaining engine gear information of the paver and the current swash plate angle of the main hydraulic pump;

[0097] Step S300: determining a target swash plate angle according to a target vibration frequency and engine status information;

[0098] Step S400: adjusting the swash plate angle of the main hydraulic pump according to the current swash plate angle and the target swash plate angle;

[0099] The engine status information includes the gear information and speed information of the engine.

[0100] In this embodiment, through steps S100 to S200, the target vibration frequency of the vibrating mechanism of the paver is obtained to determine the target value; by obtaining the engine status information of the paver and the current swash plate angle of the main hydraulic pump, the current state of the paver is determined to prepare for the subsequent adjustment and control operation. Through step S300, the current gear and speed of the engine are determined through the engine gear information and speed information, and then the target swash plate angle corresponding to the target vibration frequency is determined by calculation according to the corresponding relationship between the vibration frequency, the gear and speed of the engine and the swash plate angle. Then, through step S400, the swash plate angle of the main hydraulic pump is adjusted according to the current swash plate angle and the target swash plate angle, so that the swash plate angle of the main hydraulic pump reaches the target swash plate angle, and the regulation and control operation is completed.

[0101] It can be understood that the hydraulic main pump drives the vibrating motor assembly 12 to work, and then drives the vibrating mechanism to work, so there is a certain correspondence between the flow rate of the hydraulic main pump and the vibration frequency. The target vibration frequency is set by the operator according to the construction requirements during the construction operation.

[0102] In this embodiment, the displacement of the main hydraulic pump is matched with the gear position of the engine by adjusting the swash plate angle of the main hydraulic pump, so that the flow of the main hydraulic pump is kept constant when the engine switches gears, thereby keeping the vibration frequency of the vibration mechanism at the target vibration frequency. Different adjustment control strategies are adopted for different gear positions of the engine during the adjustment control process, and the corresponding relationship between the engine speed at different gear positions and the swash plate angle and flow rate of the main hydraulic pump is distinguished to reduce or even eliminate the influence of the gear switching of the engine on the vibration frequency. The accuracy and precision of the control operation are higher, which can effectively improve the operation efficiency and quality of the mechanism.

[0103] In some embodiments of the present invention, a paver vibration control method is provided, which is applied to the paver vibration hydraulic system in any embodiment of the first aspect or the paver in any embodiment of the second aspect. Figure 6 As shown, the paver vibration control method includes:

[0104] Step S100: obtaining a target vibration frequency of a vibration mechanism of a paver;

[0105] Step S200: acquiring engine status information of the paver and the current swash plate angle of the main hydraulic pump;

[0106] Step S310: determining a target flow rate of the main hydraulic pump according to the target vibration frequency and the first corresponding relationship curve;

[0107] Step S320: determining the current gear and current speed of the engine according to the engine state information;

[0108] Step S330: determining a target swash plate angle corresponding to the target flow rate according to the current gear position and current speed of the engine and a second corresponding relationship curve;

[0109] Step S400: adjusting the swash plate angle of the main hydraulic pump according to the current swash plate angle and the target swash plate angle;

[0110] Among them, the engine status information includes the gear information and speed information of the engine; the controller of the paver vibrating hydraulic system stores a first correspondence curve between the vibration frequency of the vibrating mechanism and the flow rate of the main hydraulic pump, and a second correspondence curve between the engine speed in each gear and the swash plate angle and flow rate of the main hydraulic pump.

[0111] In this embodiment, step S300 in the above embodiment is further improved. Through step S310, the target flow of the main hydraulic pump corresponding to the target vibration frequency is determined by using the first correspondence curve between the vibration frequency and the flow of the main hydraulic pump. Through step S320, the current gear and current speed of the engine are determined, and then through step S330, the target swash plate angle corresponding to the target flow is determined by using the second correspondence between the engine speed at each gear and the swash plate angle and flow of the main hydraulic pump, that is, the target value of the angle adjustment is determined as the basis for the subsequent swash plate angle adjustment operation. By making specific and detailed limitations on the adjustment control logic, the influence of the engine gear switching on the vibration frequency adjustment operation is reduced or eliminated, so that the accuracy and precision of the final adjustment operation are further improved to be consistent with the actual use of the paver.

[0112] In some embodiments of the present invention, a paver vibration control method is provided, which is applied to the paver vibration hydraulic system in any embodiment of the first aspect or the paver in any embodiment of the second aspect. Figure 7 As shown, the paver vibration control method includes:

[0113] Step S100: obtaining a target vibration frequency of a vibration mechanism of a paver;

[0114] Step S200: acquiring engine status information of the paver and the current swash plate angle of the main hydraulic pump;

[0115] Step S310: determining a target flow rate of the main hydraulic pump according to the target vibration frequency and the first corresponding relationship curve;

[0116] Step S320: determining the current gear and current speed of the engine according to the engine state information;

[0117] Step S330: determining a target swash plate angle corresponding to the target flow rate according to the current gear position and current speed of the engine and a second corresponding relationship curve;

[0118] Step S420: determining whether the current swash plate angle is greater than a first angle threshold, and generating a first determination result;

[0119] If the first judgment result is yes, then step S430 is executed: the swash plate angle of the main hydraulic pump is reduced to within the target angle range;

[0120] If the first judgment result is no, then executing step S440: judging whether the current swash plate angle is less than a second angle threshold, and generating a second judgment result;

[0121] If the second judgment result is yes, then step S450 is executed: increasing the swash plate angle of the main hydraulic pump to within the target angle range;

[0122] If the second judgment result is no, then step S460 is executed: controlling the swash plate angle of the main hydraulic pump to maintain the current swash plate angle;

[0123] Among them, the engine status information includes the gear information and speed information of the engine; the controller of the paver vibration hydraulic system stores a first correspondence curve between the vibration frequency of the vibration mechanism and the flow of the main hydraulic pump, and a second correspondence curve between the engine speed and the swash plate angle and flow of the main hydraulic pump in each gear; the target angle range is [second angle threshold, first angle threshold], the first angle threshold = target swash plate angle + allowable error value, the second angle threshold = target swash plate angle - allowable error value.

[0124] In this embodiment, step S400 in the above embodiment is further improved. The target swash plate angle is set with an allowable error value. The difference between the swash plate angle of the main hydraulic pump and the target swash plate angle is not greater than the allowable error value, that is, when the swash plate angle is adjusted to the target angle range, it can be considered that the swash plate angle has been adjusted to the target swash plate angle, and the adjustment operation is completed. Accordingly, through step S420 and step S440, the magnitude relationship between the current swash plate angle of the main hydraulic pump and the first angle threshold and the second angle threshold is judged respectively, so as to determine whether the current swash plate angle is within the target angle range. If the current swash plate angle is outside the target angle range, when the current swash plate angle is greater than the first angle threshold, it indicates that the current swash plate angle is too large. Through step S430, the swash plate angle of the main hydraulic pump is reduced to make the swash plate angle enter the target angle range; when the current swash plate angle is less than the second angle threshold, it indicates that the swash plate angle of the main hydraulic pump is too small. Through step S450, the swash plate angle is increased to make the swash plate angle of the main hydraulic pump enter the target angle range. If the current swash plate angle is greater than or equal to the second angle threshold and less than or equal to the first angle threshold, it indicates that the swash plate angle of the main hydraulic pump has entered the target angle range. At this time, step S460 is performed to maintain the swash plate angle of the main hydraulic pump at the current swash plate angle.

[0125] Through the above adjustment operation, the swash plate angle of the main hydraulic pump can be matched with the target swash plate angle, thereby completing the adjustment operation of the swash plate angle of the main hydraulic pump, so that the flow of the main hydraulic pump is kept constant when the engine switches gears, and the vibration frequency of the vibrating mechanism is kept at the target vibration frequency. In addition, an allowable error range is set during the adjustment operation to keep the adjustment control operation at an appropriate sensitivity to match the actual use of the paver, reduce frequent adjustment operations caused by small fluctuations in the swash plate angle, and help improve the stability of the hydraulic system operation.

[0126] In the embodiment of the fourth aspect of the present invention, an electronic device is also provided, which may include: a processor, a communication interface, a memory and a communication bus, wherein the processor, the communication interface and the memory communicate with each other through the communication bus. The processor may call the logic instructions in the memory to execute the paver vibration control method in any of the above embodiments. The electronic device in this embodiment has all the beneficial effects of the paver vibration control method in any of the above embodiments, which will not be repeated here.

[0127] In addition, the logic instructions in the above-mentioned memory can be implemented in the form of software functional units. When the logic instructions are implemented in the form of software functional units and sold or used as independent products, they can be stored in a computer-readable storage medium. Based on such an understanding, the technical solution of the present invention, in essence, or the part that contributes to the prior art or the part of the technical solution, can be embodied in the form of a software product, and the computer software product is stored in a storage medium, including a number of instructions to enable a computer device (which can be a personal computer, a server, or a network device, etc.) to perform all or part of the steps of the paver vibration control method of each embodiment of the present invention. The aforementioned storage medium includes: U disk, mobile hard disk, read-only memory (ROM, Read-Only Memory), random access memory (RAM, Random Access Memory), disk or optical disk and other media that can store program codes.

[0128] In the embodiment of the fifth aspect of the present invention, a computer-readable storage medium is further provided, on which a computer program is stored, and when the computer program is executed by a processor, the paver vibration control method in any of the above embodiments is implemented. The computer-readable storage medium in this embodiment has all the beneficial effects of the paver vibration control method in any of the above embodiments, which will not be repeated here.

[0129] The basic principle of the present invention is described above in conjunction with specific embodiments. However, it should be pointed out that the advantages, strengths, effects, etc. mentioned in the present invention are only examples and not limitations, and it cannot be considered that these advantages, strengths, effects, etc. must be possessed by each embodiment of the present invention. In addition, the specific details disclosed above are only for the purpose of illustration and facilitation of understanding, rather than limitation, and the above details do not limit the present invention to being implemented by adopting the above specific details.

[0130] The block diagrams of the devices, apparatuses, equipment, and systems involved in the present invention are only illustrative examples and are not intended to require or imply that they must be connected, arranged, and configured in the manner shown in the block diagrams. As will be appreciated by those skilled in the art, these devices, apparatuses, equipment, and systems can be connected, arranged, and configured in any manner. Words such as "including", "comprising", "having", etc. are open words, referring to "including but not limited to", and can be used interchangeably with them. The words "or" and "and" used here refer to the words "and / or" and can be used interchangeably with them, unless the context clearly indicates otherwise. The words "such as" used here refer to the phrase "such as but not limited to", and can be used interchangeably with them. It should also be noted that in the apparatus and equipment of the present invention, the components can be decomposed and / or recombined. These decompositions and / or recombinations should be regarded as equivalents of the present invention.

[0131] The computer program product of the present invention may be written in any combination of one or more programming languages ​​to write program codes for performing the operations of the embodiments of the present application, including object-oriented programming languages ​​such as Java, C++, etc., and conventional procedural programming languages ​​such as "C" language or similar programming languages. The program code may be executed entirely on the user computing device, partially on the user computing device, as a separate software package, partially on the user computing device and partially on a remote computing device, or entirely on a remote computing device or server.

[0132] The readable storage medium in the present invention can adopt any combination of one or more readable media. The readable medium can be a readable signal medium or a readable storage medium. The readable storage medium can include, for example, but is not limited to, a system, device or device of electricity, magnetism, light, electromagnetic, infrared, or semiconductor, or any combination of the above. More specific examples (non-exhaustive list) of readable storage media include: an electrical connection with one or more wires, a portable disk, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disk read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the above. The above description has been given for the purpose of illustration and description. In addition, this description is not intended to limit the embodiments of the present application to the form disclosed herein. Although multiple exemplary aspects and embodiments have been discussed above, those skilled in the art will recognize some of its variations, modifications, changes, additions and sub-combinations.

[0133] The above description of the disclosed aspects is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these aspects will be readily apparent to those skilled in the art, and the general principles defined herein may be applied to other aspects without departing from the scope of the present invention. Therefore, the present invention is not intended to be limited to the aspects shown herein, but rather to the widest scope consistent with the principles and novel features of the present invention.

[0134] The above are only preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, etc. made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A paver vibrating hydraulic system, characterized in that: include: A hydraulic pump assembly (11), comprising a main hydraulic pump (111) with a swash plate (1111), wherein the main hydraulic pump (111) is drivingly connected to an engine (212); A vibrating motor assembly (12), wherein the vibrating motor assembly (12) is connected to the main hydraulic pump (111) via a pipeline to form a hydraulic circuit; an adjustment assembly (13) connected to a pipeline between the main hydraulic pump (111) and the vibrating motor assembly (12) through a pipeline, the adjustment assembly (13) being provided with an adjustment mechanism (132) drivingly connected to a swash plate (1111) of the main hydraulic pump (111), the adjustment mechanism (132) being adapted to drive the swash plate (1111) to swing so as to adjust the displacement of the main hydraulic pump (111); The pipeline connecting the main hydraulic pump (111) and the vibrating motor assembly (12) comprises a first main path (151) and a second main path (152); the main hydraulic pump (111) is a plunger pump having an oil drain port and two oil pump ports, the oil drain port of the main hydraulic pump (111) is in communication with an oil tank (110), an angle sensor (1112) is provided on the swash plate (1111) of the main hydraulic pump (111), and the angle sensor (1112) is in communication with a controller (14); The vibrating motor assembly (12) comprises a hydraulic motor (121) having two motor oil ports, the output end of the hydraulic motor (121) being suitable for transmission connection with the vibrating mechanism (22) of the paving machine, one motor oil port of the hydraulic motor (121) being connected to a pump oil port of the main hydraulic pump (111) through the first main path (151), and the other motor oil port of the hydraulic motor (121) being connected to the other pump oil port of the main hydraulic pump (111) through the second main path (152); A controller (14) is in communication with the main hydraulic pump (111) and the adjustment component (13), wherein the controller stores a first corresponding relationship curve between the vibration frequency of the vibration mechanism and the flow rate of the main hydraulic pump and a second corresponding relationship curve between the engine speed at each gear position and the swash plate angle and displacement of the main hydraulic pump; The controller (14) is adapted to control the adjustment component (13) to adjust the current swash plate angle of the main hydraulic pump (111) according to the first corresponding relationship curve, the second corresponding relationship curve, the target vibration frequency of the vibration mechanism and the engine status information of the paver, so as to keep the flow of the main hydraulic pump (111) constant after the engine switches gears.

2. The paver vibrating hydraulic system according to claim 1, characterized in that: The adjustment component (13) comprises: An electric proportional servo valve (131) is connected to the first main path (151) and the second main path (152) through pipelines, and is communicatively connected to the controller (14); The regulating mechanism (132) comprises a regulating oil cylinder (1321), wherein the regulating oil cylinder (1321) is drivingly connected to the valve core of the electric proportional servo valve (131) and the swash plate (1111) of the main hydraulic pump (111), and the regulating oil cylinder (1321) is suitable for performing telescopic movement driven by the valve core of the electric proportional servo valve (131) to adjust the swash plate angle of the main hydraulic pump (111).

3. The paver vibrating hydraulic system according to claim 2, characterized in that: The adjustment component (13) further comprises: A first one-way overflow valve (133) is arranged in a pipeline connecting the electric proportional servo valve (131) to the first main path (151), and an overflow oil inlet of the first one-way overflow valve (133) is connected to the first main path (151); A second one-way overflow valve (134) is provided in a pipeline connecting the electric proportional servo valve (131) to the second main path (152), and an overflow oil inlet of the second one-way overflow valve (134) is connected to the second main path (152); The one-way conduction direction of the first one-way overflow valve (133) and the second one-way overflow valve (134) is from their respective overflow oil outlets to their overflow oil inlets, and the overflow oil outlet of the second one-way overflow valve (134) is connected to the overflow oil outlet of the first one-way overflow valve (133) through a pipeline, and is connected to the electric proportional servo valve (131) through a common pipeline (153).

4. The paver vibrating hydraulic system according to claim 3, characterized in that: The electric proportional servo valve (131) is provided with a first valve port (1311), a second valve port (1312), a third valve port (1313) and a fourth valve port (1314); the first valve port (1311) is connected to the oil tank (110) through a pipeline, and the second valve port (1312) is connected to the common pipeline (153); The adjustment component (13) further comprises: a first pressure cut-off valve (137), wherein an oil inlet of the first pressure cut-off valve (137) is connected to the first main circuit (151) through a pipeline, and an oil outlet of the first pressure cut-off valve (137) is connected to a third valve port (1313) of the electric proportional servo valve (131) and a rod chamber of the regulating oil cylinder (1321) through a pipeline; a second pressure cut-off valve (138), wherein an oil inlet of the second pressure cut-off valve (138) is connected to the second main path (152) through a pipeline, and an oil outlet of the second pressure cut-off valve (138) is connected to a fourth valve port (1314) of the electric proportional servo valve (131) and a rodless chamber of the regulating oil cylinder (1321) through a pipeline; The pressure thresholds of the first pressure cut-off valve (137) and the second pressure cut-off valve (138) are both greater than the pressure thresholds of the first one-way relief valve (133) and the second one-way relief valve (134).

5. The paver vibrating hydraulic system according to claim 4, characterized in that: The hydraulic pump assembly (11) further comprises: An oil replenishment pump (112) is transmission-connected to the main hydraulic pump (111), and an oil inlet of the oil replenishment pump (112) is connected to the oil tank (110); The adjustment component (13) further comprises: A high-pressure filter (136), wherein an oil inlet of the high-pressure filter (136) is connected to an oil outlet of the oil replenishment pump (112) through a pipeline, and an oil outlet of the high-pressure filter (136) is connected to the common pipeline (153) through a pipeline; A third overflow valve (135), wherein an oil inlet of the third overflow valve (135) is connected to the common pipeline (153) through a pipeline, and an oil outlet of the third overflow valve (135) is connected to the oil tank (110) through a pipeline; The main hydraulic pump (111), the charge pump (112), the electric proportional servo valve (131), the first one-way relief valve (133), the second one-way relief valve (134), the third relief valve (135), the first pressure cut-off valve (137), and the second pressure cut-off valve (138) are arranged in an integrated pump body; And / or, the vibrating motor assembly (12) further comprises: a fourth overflow valve (122), wherein an oil outlet of the fourth overflow valve (122) is connected to the oil tank (110) via a pipeline; a reversing valve (123), wherein different valve ports on the reversing valve (123) are respectively connected to the first main path (151), the second main path (152) and the oil inlet of the fourth overflow valve (122) through pipelines, and the reversing valve (123) is suitable for controlling the oil inlet of the fourth overflow valve (122) to be connected to the first main path (151) or the second main path (152), or controlling the oil inlet of the fourth overflow valve (122) to be closed; The hydraulic motor (121), the fourth overflow valve (122) and the reversing valve (123) are arranged in an integrated body.

6. A paver, characterized in that: include: A vehicle body (21), wherein an engine (212) is provided on the vehicle body (21); A vibrating mechanism (22) connected to the vehicle body (21); The paver vibrating hydraulic system according to any one of claims 1 to 5 is arranged on the vehicle body (21).

7. A paver vibration control method, used in the paver vibration hydraulic system according to any one of claims 1 to 5 or the paver according to claim 6, characterized in that: The paver vibration control method comprises: Step S100: obtaining a target vibration frequency of a vibration mechanism of a paver; Step S200: acquiring engine status information of the paver and a current swash plate angle of a main hydraulic pump; Step S300: determining a target swash plate angle according to the target vibration frequency, the engine state information, a first correspondence curve between the vibration frequency and the flow rate of the main hydraulic pump, and a second correspondence curve between the engine speed at each gear and the swash plate angle and displacement of the main hydraulic pump; Step S400: adjusting the swash plate angle of the main hydraulic pump according to the current swash plate angle and the target swash plate angle, so as to keep the flow rate of the main hydraulic pump constant after the engine shifts gears; The engine status information includes gear information and speed information of the engine.

8. The paver vibration control method according to claim 7, characterized in that: The step S300: determining a target swash plate angle according to the target vibration frequency, the engine state information, a first correspondence curve between the vibration frequency and the flow rate of the main hydraulic pump, and a second correspondence curve between the engine speed at each gear and the swash plate angle and displacement of the main hydraulic pump, comprises: Step S310: determining a target flow rate of the main hydraulic pump according to the target vibration frequency and the first corresponding relationship curve; Step S320: determining the current gear position and current speed of the engine according to the engine state information; Step S330: Determine the target swash plate angle corresponding to the target flow rate according to the current gear position and current speed of the engine and the second corresponding relationship curve.

9. The paver vibration control method according to claim 8, characterized in that: The step S400: adjusting the swash plate angle of the main hydraulic pump according to the current swash plate angle and the target swash plate angle, comprises: Step S420: determining whether the current swash plate angle is greater than a first angle threshold, and generating a first determination result; If the first judgment result is yes, executing step S430: reducing the swash plate angle of the main hydraulic pump to within a target angle range; If the first judgment result is no, executing step S440: judging whether the current swash plate angle is less than a second angle threshold, and generating a second judgment result; If the second judgment result is yes, executing step S450: increasing the swash plate angle of the main hydraulic pump to within the target angle range; If the second judgment result is no, executing step S460: controlling the swash plate angle of the main hydraulic pump to maintain the current swash plate angle; The target angle range is [second angle threshold, first angle threshold], the first angle threshold=target swash plate angle+allowable error value, and the second angle threshold=target swash plate angle-allowable error value.

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