Excavator swing motor, hydraulic system, and control method

Abstract

The application provides a excavator rotary motor, a hydraulic system and a control method, and the structure of the excavator rotary motor comprises a motor body, a first oil port and a second oil port, the first oil port is communicated with a first cavity of the motor body, and the second oil port is communicated with a second cavity of the motor body; a proportional valve is communicated with the first oil port and the second oil port; a control detection part is connected to the motor body, the control detection part can detect the pressure of the first oil port and the second oil port, the control detection part is in conductive connection with the proportional valve, and the control detection part can control the opening degree of the proportional valve; a first check valve is communicated with the first cavity and an oil tank of the excavator; and a second check valve is communicated with the second cavity and the oil tank of the excavator. The excavator rotary motor, the hydraulic system and the control method can solve the problem that the existing excavator rotary motor is difficult to meet the use requirement.

Description

Technical Field

[0001] This application relates to the field of excavator technology, and in particular to an excavator swing motor, hydraulic system and control method. Background Technology

[0002] Currently available excavator swing motors, in addition to the motor body, are typically equipped with two relief valves, two replenishing check valves, and two anti-sway valves. The relief valves provide torque for starting and braking the swing motor and protect it from overpressure operation. The replenishing check valves replenish oil to the low-pressure chamber of the swing motor. The anti-sway valves eliminate reverse swaying caused by inertia and oil compression during braking.

[0003] Existing excavator swing motors have non-adjustable relief valve settings for both starting and braking, requiring the same relief valve for both. This lack of adjustable starting and braking performance hinders personalized and precise optimization of these actions. Manually adjusting the relief valve pressure necessitates simultaneous adjustment of both starting and braking torques, a cumbersome process that cannot differentiate between starting and braking torques. Furthermore, the inherent characteristics of the relief valve result in varying pressures at different flow rates, leading to varying starting pressures for the swing motor at different speeds. Current swing motors cannot achieve maximum starting torque at low flow rates. Additionally, existing anti-sway valves only detect pressure acceleration, making their effectiveness highly dependent on valve performance, and their anti-sway effect is not adjustable. Summary of the Invention

[0004] In view of this, the purpose of this application is to provide an excavator swing motor, hydraulic system and control method to solve the problem that existing excavator swing motors cannot meet the usage requirements.

[0005] According to a first aspect of the present invention, an excavator swing motor is provided, wherein the excavator swing motor comprises: a motor body having a first oil port and a second oil port, the first oil port being connected to a first cavity of the motor body and the second oil port being connected to a second cavity of the motor body; a proportional valve being connected to the first oil port and the second oil port; a control detection unit being connected to the motor body, the control detection unit being capable of detecting the pressure of the first oil port and the second oil port, the control detection unit being electrically connected to the proportional valve, and the control detection unit being capable of controlling the opening degree of the proportional valve; a first check valve being connected to the first cavity and the excavator's fuel tank; and a second check valve being connected to the second cavity and the excavator's fuel tank.

[0006] Preferably, the control and detection unit includes: a processor, wherein the proportional valve is provided with a first electromagnet, the processor is electrically connected to the first electromagnet, and the processor is capable of controlling the opening degree of the proportional valve; a first pressure sensor installed at the pressure measuring port of the motor body, the first pressure sensor being used to detect the pressure of the first oil port; a second pressure sensor installed at the pressure measuring port of the motor body, the second pressure sensor being used to detect the pressure of the second oil port; and a comparator electrically connected to the first pressure sensor and the second pressure sensor, the comparator being electrically connected to the processor.

[0007] According to a second aspect of the invention, a hydraulic system is provided, wherein the hydraulic system includes an excavator swing motor as described above.

[0008] Preferably, the hydraulic system further includes: a slewing valve connected to the oil tank, with the first oil port and the second oil port connected to the slewing valve, and the processor electrically connected to the slewing valve; a main pump connected to the slewing valve and the main pump connected to the oil tank; and an engine connected to the main pump for driving the main pump to supply oil to the slewing valve.

[0009] Preferably, the directional valve is equipped with a second electromagnet and a third electromagnet. When the second electromagnet is energized, the hydraulic oil in the directional valve can flow into the first chamber through the first oil port. When the third electromagnet is energized, the hydraulic oil in the directional valve can flow into the second chamber through the second oil port. The processor is electrically connected to the second electromagnet and the third electromagnet respectively, and is used to detect the energization status of the second electromagnet and the third electromagnet.

[0010] Preferably, the first check valve and the second check valve are connected to the oil tank through the directional valve, and a back pressure valve is provided between the directional valve and the oil tank.

[0011] According to a third aspect of the present invention, a control method for a hydraulic system is provided, wherein the hydraulic system is as described above, and the control method for the hydraulic system includes: controlling the energization of the second electromagnet and the third electromagnet and the opening degree of the proportional valve to realize the starting, braking and anti-swaying of the excavator swing motor.

[0012] Preferably, when the excavator's swing motor starts rotating clockwise, the second electromagnet of the swing reversing valve is energized, and hydraulic oil enters the first chamber of the motor body through the first port. The second port serves as the return port, and the first chamber becomes a high-pressure chamber, driving the motor body to rotate clockwise. At this time, the starting value of the first electromagnet is set to Pa. The first pressure sensor detects the pressure of the first chamber in real time. When the pressure of the first chamber is higher than Pa, the proportional valve opens and connects the first chamber and the second chamber. When the pressure of the first chamber is lower than Pa, the proportional valve closes. When the excavator's swing motor starts rotating counterclockwise, the third electromagnet of the swing reversing valve is energized, and hydraulic oil enters the second chamber of the motor body through the second port. The first port serves as the return port, and the second chamber becomes a high-pressure chamber, driving the motor body to rotate counterclockwise. At this time, the starting value of the first electromagnet is set to Pb. The second pressure sensor detects the pressure of the second chamber in real time. When the pressure of the second chamber is higher than Pb, the proportional valve opens and connects the first chamber and the second chamber. When the pressure of the second chamber is lower than Pb, the proportional valve closes.

[0013] Preferably, when the excavator's swing motor rotates clockwise for braking, the second electromagnet of the swing reversing valve is de-energized, the flow of the main pump is cut off, and the motor body tends to rotate clockwise due to inertia. The pressure in the first chamber decreases, becoming a low-pressure chamber, while the pressure in the second chamber increases, becoming a high-pressure chamber. At this time, the starting value of the first electromagnet is set to Pc. The second pressure sensor detects the pressure in the second chamber in real time. When the pressure in the second chamber is higher than Pc, the proportional valve opens and connects the first and second chambers. When the pressure in the second chamber is lower than Pc, the proportional valve closes. When the excavator's swing motor rotates counterclockwise for braking, the third electromagnet of the swing reversing valve is de-energized, the flow of the main pump is cut off, and the motor body tends to rotate counterclockwise due to inertia. The pressure in the second chamber decreases, becoming a low-pressure chamber, while the pressure in the first chamber increases, becoming a high-pressure chamber. At this time, the starting value of the first electromagnet is set to Pd. The first pressure sensor detects the pressure in the first chamber in real time. When the pressure in the first chamber is higher than Pd, the proportional valve opens and connects the first and second chambers. When the pressure in the first chamber is lower than Pd, the proportional valve closes.

[0014] Preferably, when the excavator's swing motor rotates clockwise to prevent swaying, the braking process causes the motor body to tend to rotate counterclockwise. The pressure in the first chamber rises, becoming a high-pressure chamber, while the pressure in the second chamber decreases, becoming a low-pressure chamber. At this time, the given current value of the first electromagnet is adjusted according to the pressure difference between the first and second chambers. The first pressure sensor detects the pressure in the first chamber in real time, and the second pressure sensor detects the pressure in the second chamber in real time. The opening degree of the proportional valve is proportional to the pressure difference between the first and second chambers. Conversely, when the excavator's swing motor rotates counterclockwise to prevent swaying, the braking process causes the motor body to tend to rotate clockwise. The pressure in the first chamber decreases, becoming a low-pressure chamber, while the pressure in the second chamber rises, becoming a high-pressure chamber. At this time, the given current value of the first electromagnet is adjusted according to the pressure difference between the first and second chambers. The first pressure sensor detects the pressure in the first chamber in real time, and the second pressure sensor detects the pressure in the second chamber in real time. The opening degree of the proportional valve is proportional to the pressure difference between the first and second chambers.

[0015] The excavator swing motor, hydraulic system, and control method of this invention include a motor body with a first oil port and a second oil port. The first oil port is connected to a first chamber of the motor body, and the second oil port is connected to a second chamber of the motor body. A proportional valve is connected to both the first and second oil ports. A control and detection unit is located in the motor body. The control and detection unit can detect the pressure of the first and second oil ports. Furthermore, the control and detection unit is electrically connected to the proportional valve and can control the opening degree of the proportional valve. Therefore, the control and detection unit can adjust the opening degree of the proportional valve according to the pressure of the first and second oil ports, allowing the proportional valve to replace the original relief valve and anti-sway valve, achieving adjustable starting torque and braking torque, as well as adjustable anti-sway effect. A first check valve is connected to the first chamber and the excavator's oil tank, and a second check valve is connected to the second chamber and the excavator's oil tank. The first and second check valves are used to replenish oil to the low-pressure chamber during braking. This effectively solves the problem that existing excavator swing motors cannot meet usage requirements.

[0016] To make the above-mentioned objectives, features and advantages of this application more apparent and understandable, preferred embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0017] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this application and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a schematic diagram of the excavator rotary motor and hydraulic system according to the present invention.

[0019] Figure 2 This is another schematic diagram of the excavator rotary motor and hydraulic system according to the present invention.

[0020] Reference numerals: 1-Motor body; 11-First oil port; 12-Second oil port; 2-Proportional valve; 21-First electromagnet; 3-First check valve; 4-Second check valve; 50-Processor; 51-First pressure sensor; 52-Second pressure sensor; 53-First analog-to-digital converter; 54-Second analog-to-digital converter; 55-Comparator; 6-Reverse directional valve; 61-Back pressure valve; 62-Second electromagnet; 63-Third electromagnet; 70-Main pump; 71-Engine; 8-Fuel tank. Detailed Implementation

[0021] The following detailed embodiments are provided to help the reader gain a comprehensive understanding of the methods, apparatus, and / or systems described herein. However, various changes, modifications, and equivalents of the methods, apparatus, and / or systems described herein will be apparent after understanding the disclosure of this application. For example, the order of operations described herein is merely illustrative and is not limited to the order set forth herein; changes that will be apparent after understanding the disclosure of this application are possible, except for operations that must occur in a specific order. Furthermore, for clarity and brevity, descriptions of features known in the art may be omitted.

[0022] The features described herein may be implemented in different forms and should not be construed as being limited to the examples described herein. Rather, the examples described herein have been provided merely to illustrate some of the many feasible ways of implementing the methods, apparatus, and / or systems described herein that will be apparent upon understanding the disclosure of this application.

[0023] Throughout the specification, when an element (such as a layer, region, or substrate) is described as being "on" another element, "connected to" another element, "bonded to" another element, "on" another element, or "covering" another element, it may be directly "on" another element, "connected to" another element, "bonded to" another element, "on" another element, or "covering" another element, or there may be one or more other elements in between. In contrast, when an element is described as being "directly on" another element, "directly connected to" another element, "directly bonded to" another element, "directly on" another element, or "directly covering" another element, there may be no other elements in between.

[0024] As used herein, the term “and / or” includes any one of the relevant items listed and any combination of any two or more items.

[0025] Although terms such as “first,” “second,” and “third” may be used herein to describe individual components, assemblies, regions, layers, or parts, these components, assemblies, regions, layers, or parts are not limited by these terms. Rather, these terms are used only to distinguish one component, assembly, region, layer, or part from another. Therefore, without departing from the teachings of the examples described herein, the first component, assembly, region, layer, or part referred to as the second component, assembly, region, layer, or part may also be referred to as the second component, assembly, region, layer, or part.

[0026] For ease of description, spatial relation terms such as “above,” “upper,” “below,” and “lower” are used herein to describe the relationship between one element and another, as shown in the accompanying drawings. Such spatial relation terms are intended to include not only the orientation depicted in the drawings but also different orientations of the device during use or operation. For example, if the device in the drawings is flipped, an element described as being “above” or “upper” relative to another element will subsequently be “below” or “lower” relative to that other element. Therefore, the term “above” includes both “above” and “below” orientations depending on the spatial orientation of the device. The device may also be positioned in other ways (e.g., rotated 90 degrees or in other orientations), and the spatial relation terms used herein will be interpreted accordingly.

[0027] The terminology used herein is for the purpose of describing various examples only and is not intended to limit the examples. Unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. The terms “comprising,” “including,” and “having” enumerate the stated features, quantities, operations, components, elements, and / or combinations thereof, but do not exclude the presence or addition of one or more other features, quantities, operations, components, elements, and / or combinations thereof.

[0028] Variations in the shapes shown in the accompanying drawings may occur due to manufacturing techniques and / or tolerances. Therefore, the examples described herein are not limited to the specific shapes shown in the accompanying drawings, but include changes in shape that may occur during manufacturing.

[0029] The features of the examples described herein can be combined in various ways that will be apparent upon understanding the disclosure of this application. Furthermore, although the examples described herein have a wide variety of constructions, other constructions are possible, as will be apparent upon understanding the disclosure of this application.

[0030] like Figure 1 and Figure 2 As shown, according to a first aspect of the present invention, an excavator swing motor is provided, the excavator swing motor including a motor body 1, a proportional valve 2, a control and detection unit, a first check valve 3 and a second check valve 4.

[0031] In the following description, reference will be made to Figure 1 and Figure 2 The specific structure of the aforementioned components of the excavator's swing motor and their connection relationships are described in detail.

[0032] like Figure 1 and Figure 2 As shown, in this embodiment, the motor body 1 may be provided with a first oil port 11 and a second oil port 12, the first oil port 11 and the second oil port 12 being used for oil inlet and oil return, respectively. The first oil port 11 may be connected to the first cavity of the motor body 1 (e.g., Figure 1 and Figure 2 As shown, the first cavity can be located on the left side of the motor body 1, and the second oil port 12 can be connected to the second cavity of the motor body 1 (e.g., ...). Figure 1 and Figure 2 As shown, the second chamber can be located on the right side of the motor body 1. A proportional valve 2 can be connected to the first oil port 11 and the second oil port 12. When the proportional valve 2 is open, the throttling channel between the first oil port 11 and the second oil port 12 is opened, connecting the first chamber and the second chamber. A first check valve 3 connects the first chamber to the excavator's fuel tank 8. A second check valve 4 connects the second chamber to the excavator's fuel tank 8. The first check valve 3 and the second check valve 4 can replenish oil to the low-pressure chamber of the motor body 1 during braking. A control detection unit can be connected to the motor body 1. The control detection unit can detect the pressure of the first oil port 11 and the second oil port 12. Furthermore, the control detection unit can also be electrically connected to the proportional valve 2, and the control detection unit can control the opening degree of the proportional valve 2, thereby controlling the communication state between the first chamber and the second chamber. Therefore, the control and detection unit can adjust the opening of the proportional valve 2 according to the pressure of the first oil port 11 and the second oil port 12, so that the proportional valve 2 can replace the original overflow valve and anti-sway valve, and can realize the adjustable starting torque and braking torque of the excavator swing motor and the adjustable anti-sway effect.

[0033] Preferred, such as Figure 1 and Figure 2As shown, in this embodiment, the controllable detection unit includes a processor 50, a first pressure sensor 51, a second pressure sensor 52, and a comparator 55. The processor 50 can be located outside the housing of the excavator's swing motor. The proportional valve 2 can be a high-response proportional valve. The proportional valve 2 can be equipped with a first electromagnet 21, and the processor 50 can be electrically connected to the first electromagnet 21. The processor 50 can control the opening degree of the proportional valve 2 by controlling the energization of the first electromagnet 21. The first pressure sensor 51 and the second pressure sensor 52 can be installed at the pressure measuring ports of the motor body 1. The first pressure sensor 51 is used to detect the pressure of the first oil port 11, and the second pressure sensor 52 is used to detect the pressure of the second oil port 12. The comparator 55 can be electrically connected to the first pressure sensor 51 and the second pressure sensor 52, and is used to process the signals transmitted by the first pressure sensor 51 and the second pressure sensor 52. More preferably, the control detection unit may also include a first analog-to-digital converter 53 and a second analog-to-digital converter 54. The first analog-to-digital converter (ADC) 53 is electrically connected to the first pressure sensor 51, and is used to convert the pressure value detected by the first pressure sensor 51 into a digital signal. The second ADC 54 is electrically connected to the second pressure sensor 52, and is used to convert the pressure value detected by the second pressure sensor 52 into a digital signal. A comparator 55 is electrically connected to both the first ADC 53 and the second ADC 54, and is also electrically connected to the processor 50. The comparator 55 is used to further process the signals from the first ADC 53 and the second ADC 54, and transmit the signals to the processor 50. Preferably, the conductive connection can be via a wire to achieve electrical signal transmission.

[0034] In addition, preferred, such as Figure 1 As shown, in this embodiment, the control and detection unit can be integrally installed with the motor body 1. Specifically, the proportional valve 2 can be integrated into the interior of the excavator's swing motor. However, this is not the only possibility. Figure 2 As shown, in this embodiment, the control and detection unit can also be externally mounted. Specifically, the proportional valve 2 can be mounted on the rear end cover of the excavator's swing motor, and the proportional valve 2 is externally connected to the first oil port 11 and the second oil port 12 of the motor body 1.

[0035] During operation, the excavator's swing motor replaces the original two overflow valves and two anti-sway valves with a proportional valve 2. This configuration results in better starting and braking performance, as well as better elimination of pressure peaks. Furthermore, the starting torque, braking torque, and anti-sway effect of the excavator's swing motor can be adjusted and changed via a control detection unit, thereby achieving electrification and intelligent control of the excavator's swing motor's starting, braking, and swaying, while simplifying the overall structure.

[0036] In addition, such as Figure 1 and Figure 2 As shown, according to a second aspect of the present invention, a hydraulic system is provided, the hydraulic system comprising an excavator swing motor as described above.

[0037] Preferred, such as Figure 1 and Figure 2 As shown, in this embodiment, the hydraulic system may further include a directional control valve 6, a main pump 70, and an engine 71. The directional control valve 6 is connected to the excavator's oil tank 8, and the first oil port 11 and the second oil port 12 of the motor body 1 are connected to the directional control valve 6. This allows hydraulic oil to flow into the motor body 1 through the directional control valve 6, and hydraulic oil in the motor body 1 can also flow out to the directional control valve 6. The directional control valve 6 may also be electrically connected to the processor 50 for transmitting electrical signals. The main pump 70 is connected to the directional control valve 6 and the oil tank 8. The engine 71 is connected to the main pump 70 to drive the main pump 70 to supply oil to the directional control valve 6.

[0038] Preferred, such as Figure 1 and Figure 2 As shown, in this embodiment, the directional valve 6 can be a three-position six-way solenoid valve. The directional valve 6 may contain a second electromagnet 62 and a third electromagnet 63. When the second electromagnet 62 is energized, the hydraulic oil in the directional valve 6 can flow into the first chamber through the first port 11 of the motor body 1. When the third electromagnet 63 is energized, the hydraulic oil in the directional valve 6 can flow into the second chamber through the second port 12 of the motor body 1. The processor 50 can be electrically connected to the second electromagnet 62 and the third electromagnet 63 respectively, thereby enabling real-time detection of the energization and de-energization of the second electromagnet 62 and the third electromagnet 63.

[0039] In addition, preferred, such as Figure 1 and Figure 2As shown, in this embodiment, the first check valve 3 and the second check valve 4 can be connected to the oil tank 8 via the reversing valve 6. Specifically, the first check valve 3 and the second check valve 4 can be connected to the reversing valve 6 via the same pipeline. A back pressure valve 61 can be provided between the reversing valve 6 and the oil tank 8, that is, the reversing valve 6 is connected to the oil tank 8 via the back pressure valve 61. The back pressure valve 61 is used to ensure that the hydraulic oil entering the housing of the reversing valve 6 has a certain pressure, so as to ensure that the hydraulic oil can be replenished to the low-pressure chamber of the motor body 1.

[0040] During operation, the engine 71 drives the main pump 70 to supply oil to the oil inlet of the motor body 1 through the slewing valve 6, thereby driving the excavator's slewing motor to rotate. The hydraulic oil in the excavator's slewing motor returns to the housing of the slewing valve 6 through the oil outlet of the motor body 1, and then returns to the oil tank 8 through the back pressure valve 61. The slewing valve 6 controls the switching of the oil inlet and outlet of the motor body 1. Preferably, when the second electromagnet 62 is energized, the motor body 1 rotates clockwise. When the third electromagnet 63 is energized, the motor body 1 rotates counterclockwise. The processor 50 can adaptively adjust the opening of the proportional valve 2 according to the pressure of the first oil port 11 and the second oil port 12 of the motor body 1, as well as the energization status of the second electromagnet 62 and the third electromagnet 63 in the slewing valve 6, to realize the functions of the overflow valve and the anti-sway valve.

[0041] Specifically, during the starting and braking process of the excavator's swing motor, when the pressure in the motor body 1 does not exceed a preset value, the first electromagnet 21 is de-energized, and the proportional valve 2 closes, equivalent to no oil overflow. When the sensor detects that the pressure exceeds the preset value, the first electromagnet 21 is energized, and the proportional valve 2 begins to open, equivalent to oil overflow. The processor 50 can transmit different magnitude current commands to the first electromagnet 21 based on the detected pressure acceleration value to control the opening of the proportional valve 2. Different openings of the proportional valve 2 are equivalent to the high-pressure chamber of the motor body 1 flowing to the low-pressure chamber through throttling orifices of different areas, thereby reducing the pressure in the high-pressure chamber and bringing it back to the preset value. When the pressure in the high-pressure chamber returns to below the preset value, the first electromagnet 21 is de-energized again, the proportional valve 2 closes, and the throttling channel is closed. This configuration not only achieves pressure limiting protection for the motor body 1 but also effectively regulates the starting and braking pressure of the excavator's swing motor, thereby improving its starting and braking performance.

[0042] Furthermore, when the electromagnet in the directional valve 6 is de-energized, the processor 50 determines that the excavator's swing motor is in a braking state. When the pressure in the first or second chamber of the motor body 1 is detected to exceed the preset value for the first time, the proportional valve 2 uses this preset value as the basis for opening and closing. When the proportional valve 2 opens, hydraulic oil flows from the high-pressure chamber to the low-pressure chamber through the proportional valve 2, thereby providing braking torque to the motor body 1. From then on, the opening of the proportional valve 2 is based on the detected pressure difference between the first and second chambers of the motor body 1, and the opening degree of the proportional valve 2 is determined according to the magnitude of the detected pressure difference. This ensures that after the excavator's swing motor completes braking, its high-pressure chamber can be quickly unloaded through the adjustable flow channel of the proportional valve 2, effectively reducing the swing of the excavator's swing motor.

[0043] Furthermore, according to a third aspect of the present invention, a control method for a hydraulic system is provided, wherein the hydraulic system is as described above. The control method includes controlling the starting, braking, and anti-swaying of the excavator's swing motor by controlling the energization of the second electromagnet 62 and the third electromagnet 63, and the opening degree of the proportional valve 2.

[0044] Preferred, such as Figure 1 and Figure 2 As shown in the embodiment, when the excavator's swing motor starts rotating clockwise, the second electromagnet 62 of the swing reversing valve 6 is energized. Hydraulic oil enters the first chamber of the motor body 1 through the first port 11, while the second port 12 serves as the return port. The first chamber becomes a high-pressure chamber, driving the motor body 1 to rotate clockwise. At this time, the starting value of the first electromagnet 21 can be set to Pa. The first pressure sensor 51 detects the pressure of the first chamber in real time. The first analog-to-digital converter 53 transmits the signal to the comparator 55 for processing. The comparator 55 finally transmits the signal to the processor 50 to control the energization of the first electromagnet 21 of the proportional valve 2. When the pressure of the first chamber is higher than Pa, the first electromagnet 21 is energized, the proportional valve 2 opens, and a throttling channel is formed between the first chamber and the second chamber. The hydraulic oil in the first chamber is unloaded to the second chamber through the throttling channel. During this process, the current of the first electromagnet 21 can be adjusted in real time according to the pressure detected by the first pressure sensor 51 to ensure that the pressure of the first chamber is maintained at Pa, thereby driving the excavator's swing motor to rotate clockwise. When the pressure in the first chamber is lower than Pa, the first electromagnet 21 is de-energized, and the proportional valve 2 closes. The return oil in the second chamber can flow to the oil tank 8 through the directional valve 6. During this process, the starting value Pa is adjustable, and the operator can adaptively adjust the Pa value according to different gears and operating conditions, making the starting process highly adjustable.

[0045] Preferably, in this embodiment, when the excavator's swing motor starts rotating counterclockwise, the third electromagnet 63 of the swing reversing valve 6 is energized, and hydraulic oil enters the second chamber of the motor body 1 through the second port 12, while the first port 11 serves as the return port. The second chamber becomes a high-pressure chamber, driving the motor body 1 to rotate counterclockwise. At this time, the starting value of the first electromagnet 21 can be set to Pb. The second pressure sensor 52 detects the pressure of the second chamber in real time, and the second analog-to-digital converter 54 transmits the signal to the comparator 55 for processing. The comparator 55 ultimately transmits the signal to the processor 50 to control the energization of the first electromagnet 21 of the proportional valve 2. When the pressure in the second chamber is higher than Pb, the first electromagnet 21 is energized, the proportional valve 2 opens, and a throttling channel is formed between the first chamber and the second chamber. The hydraulic oil in the second chamber is unloaded into the second chamber through the throttling channel. During this process, the current of the first electromagnet 21 can be adjusted in real time according to the pressure detected by the second pressure sensor 52 to ensure that the pressure in the second chamber is maintained at Pb, thereby driving the excavator's swing motor to rotate counterclockwise. When the pressure in the second chamber is lower than Pb, the first electromagnet 21 is de-energized, and the proportional valve 2 closes. The return oil in the first chamber can flow to the oil tank 8 through the directional valve 6. During this process, the starting value Pb is adjustable, and the operator can adaptively adjust the Pb value according to different gears and operating conditions.

[0046] Preferred, such as Figure 1 and Figure 2As shown in the embodiment, when the excavator's swing motor rotates clockwise for braking, the second electromagnet 62 of the swing reversing valve 6 is de-energized, and the flow of the main pump 70 is cut off. Due to inertia, the motor body 1 tends to rotate clockwise, causing the pressure in the first chamber to drop instantaneously, becoming a low-pressure chamber, while the pressure in the second chamber instantly rises, becoming a high-pressure chamber. At this time, the starting value of the first electromagnet 21 is set to Pc. The second pressure sensor 52 detects the pressure in the second chamber in real time, and the second analog-to-digital converter 54 transmits the signal to the comparator 55 for processing. The comparator 55 ultimately transmits the signal to the processor 50 to control the energization of the first electromagnet 21 of the proportional valve 2. When the pressure in the second chamber is higher than Pc, the first electromagnet 21 is energized, the proportional valve 2 opens, and a throttling channel is formed between the first and second chambers. The hydraulic oil in the second chamber is unloaded to the first chamber through the throttling channel. During this process, the current of the first electromagnet 21 can be adjusted in real time according to the pressure detected by the second pressure sensor 52 to ensure that the pressure in the second chamber is maintained at Pc, providing braking torque for the excavator's swing motor. During braking, the hydraulic oil in the housing of the directional valve 6 can replenish the first chamber through the first check valve 3, and the second chamber can replenish the first chamber through the throttling channel of the proportional valve 2. Furthermore, the starting value Pc is adjustable during this process, allowing the operator to adapt the Pc value according to different gears and operating conditions, thus providing good adjustability for the braking process.

[0047] Preferably, in this embodiment, when the excavator's swing motor rotates counterclockwise for braking, the third electromagnet 63 of the swing reversing valve 6 is de-energized, and the flow of the main pump 70 is cut off. Due to inertia, the motor body 1 tends to rotate clockwise, causing the pressure in the first chamber to rise instantaneously, becoming a high-pressure chamber, and the pressure in the second chamber to drop instantaneously, becoming a low-pressure chamber. At this time, the starting value of the first electromagnet 21 is set to Pd. The first pressure sensor 51 detects the pressure in the first chamber in real time, and the first analog-to-digital converter 53 transmits the signal to the comparator 55 for processing. The comparator 55 ultimately transmits the signal to the processor 50 to control the energization of the first electromagnet 21 of the proportional valve 2. When the pressure in the first chamber is higher than Pd, the first electromagnet 21 is energized, the proportional valve 2 opens, and a throttling channel is formed between the first and second chambers. The hydraulic oil in the first chamber is unloaded to the second chamber through the throttling channel. During this process, the current of the first electromagnet 21 can be adjusted in real time according to the pressure detected by the first pressure sensor 51 to ensure that the pressure in the first chamber remains at Pd, providing braking torque for the excavator's swing motor. During braking, the hydraulic oil in the housing of the directional valve 6 can replenish the second chamber through the second check valve 4, and the first chamber can replenish the second chamber through the throttling channel of the proportional valve 2. Additionally, the starting value Pd is adjustable during this process, allowing the operator to adapt the Pd value according to different gear positions and operating conditions.

[0048] Preferred, such as Figure 1 and Figure 2 As shown in the embodiment, when the excavator's swing motor rotates clockwise to prevent swaying, the braking process causes the motor body 1 to tend to rotate counterclockwise. The pressure in the first chamber rises, becoming a high-pressure chamber, while the pressure in the second chamber decreases, becoming a low-pressure chamber. At this time, the set current value of the first electromagnet 21 is adjusted according to the pressure difference between the first and second chambers. The first pressure sensor 51 detects the pressure in the first chamber in real time. The second pressure sensor 52 detects the pressure in the second chamber in real time. When the processor 50 determines that a pressure difference exists between the first and second chambers, the first electromagnet 21 is energized, and the proportional valve 2 opens, forming a throttling channel between the first and second chambers. The opening degree of the proportional valve 2 can be proportional to the pressure difference between the first and second chambers; that is, the set current value of the first electromagnet 21 is adjusted according to the magnitude of the pressure difference, thereby indirectly adjusting the size of the throttling channel to quickly unload the high-pressure chamber. During this process, the anti-swaying process and effect can be adjusted by adjusting the setting value of the proportional valve 2 opening to adapt to different driving experiences.

[0049] Preferred, such as Figure 1 and Figure 2 As shown in the embodiment, when the excavator's swing motor rotates counterclockwise to prevent swaying, the braking process causes the motor body 1 to tend to rotate clockwise. The pressure in the first chamber decreases, becoming a low-pressure chamber, while the pressure in the second chamber increases, becoming a high-pressure chamber. At this time, the given current value of the first electromagnet 21 is adjusted according to the pressure difference between the first and second chambers. The first pressure sensor 51 detects the pressure in the first chamber in real time. The second pressure sensor 52 detects the pressure in the second chamber in real time. When the processor 50 determines that a pressure difference exists between the first and second chambers, the first electromagnet 21 is energized, and the proportional valve 2 opens, forming a throttling channel between the first and second chambers. The opening degree of the proportional valve 2 can be proportional to the pressure difference between the first and second chambers; that is, the given current value of the first electromagnet 21 is adjusted according to the magnitude of the pressure difference, thereby indirectly adjusting the size of the throttling channel to quickly unload the high-pressure chamber.

[0050] Finally, it should be noted that the above-described embodiments are merely specific implementations of this application, used to illustrate the technical solutions of this application, and not to limit them. The protection scope of this application is not limited thereto. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that any person skilled in the art can still modify or easily conceive of changes to the technical solutions described in the foregoing embodiments, or make equivalent substitutions for some of the technical features, within the technical scope disclosed in this application. Such modifications, changes, or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of this application, and should all be covered within the protection scope of this application. Therefore, the protection scope of this application should be determined by the protection scope of the claims.

Claims

1. A swing motor for an excavator, installed in an excavator, characterized in that, The excavator swing motor includes: The motor body (1) is provided with a first oil port (11) and a second oil port (12). The first oil port (11) is connected to the first cavity of the motor body (1), and the second oil port (12) is connected to the second cavity of the motor body (1). A proportional valve (2) is connected to the first oil port (11) and the second oil port (12); The control detection unit is connected to the motor body (1). The control detection unit can detect the pressure of the first oil port (11) and the second oil port (12). The control detection unit is electrically connected to the proportional valve (2). The control detection unit can control the opening degree of the proportional valve (2). A first one-way valve (3) is connected to the first chamber and the excavator's fuel tank (8); and The second check valve (4) is connected to the second chamber and the oil tank (8) of the excavator. The control and detection unit includes: The processor (50) is capable of controlling the opening degree of the proportional valve (2); The first pressure sensor (51) is used to detect the pressure of the first oil port (11); The second pressure sensor (52) is used to detect the pressure of the second oil port (12); and The comparator (55) is electrically connected to the first pressure sensor (51) and the second pressure sensor (52), and the comparator (55) is electrically connected to the processor (50).

2. The excavator swing motor according to claim 1, characterized in that, The proportional valve (2) is equipped with a first electromagnet (21), and the processor (50) is electrically connected to the first electromagnet (21). The first pressure sensor (51) is installed at a pressure port of the motor body (1); The second pressure sensor (52) is installed at another pressure port of the motor body (1).

3. A hydraulic system, characterized in that, The hydraulic system includes the excavator swing motor as described in claim 2.

4. The hydraulic system according to claim 3, characterized in that, The hydraulic system also includes: A reversing valve (6) is connected to the oil tank (8), the first oil port (11) and the second oil port (12) are connected to the reversing valve (6), and the processor (50) is electrically connected to the reversing valve (6); The main pump (70) is connected to the directional valve (6), and the main pump (70) is connected to the oil tank (8); and An engine (71) is connected to the main pump (70) and is used to drive the main pump (70) to supply oil to the directional valve (6).

5. The hydraulic system according to claim 4, characterized in that, The directional valve (6) is equipped with a second electromagnet (62) and a third electromagnet (63). When the second electromagnet (62) is energized, the hydraulic oil in the directional valve (6) can flow into the first chamber through the first oil port (11). When the third electromagnet (63) is energized, the hydraulic oil in the directional valve (6) can flow into the second chamber through the second oil port (12). The processor (50) is electrically connected to the second electromagnet (62) and the third electromagnet (63) respectively, and is used to detect the energization status of the second electromagnet (62) and the third electromagnet (63).

6. The hydraulic system according to claim 5, characterized in that, The first check valve (3) and the second check valve (4) are connected to the oil tank (8) through the directional valve (6), and a back pressure valve (61) is provided between the directional valve (6) and the oil tank (8).

7. A control method for a hydraulic system, characterized in that, The hydraulic system is the hydraulic system of claim 6, and the control method of the hydraulic system includes: controlling the energization of the second electromagnet (62) and the third electromagnet (63) and the opening of the proportional valve (2) to realize the starting, braking and anti-swaying of the excavator swing motor.

8. The control method for a hydraulic system according to claim 7, characterized in that, When the excavator's slewing motor starts by rotating clockwise, the second electromagnet (62) of the slewing reversing valve (6) is energized, and hydraulic oil enters the first chamber of the motor body (1) through the first oil port (11). The second oil port (12) serves as the return oil port, and the first chamber becomes a high-pressure chamber, driving the motor body (1) to rotate clockwise. At this time, the starting value of the first electromagnet (21) is set to Pa. The first pressure sensor (51) detects the pressure of the first chamber in real time. When the pressure of the first chamber is higher than Pa, the proportional valve (2) opens and connects the first chamber and the second chamber. When the pressure of the first chamber is lower than Pa, the proportional valve (2) closes. When the excavator's slewing motor starts by rotating counterclockwise, the third electromagnet (63) of the slewing reversing valve (6) is energized, and hydraulic oil enters the second chamber of the motor body (1) through the second oil port (12). The first oil port (11) serves as the return oil port, and the second chamber becomes a high-pressure chamber, driving the motor body (1) to rotate counterclockwise. At this time, the starting value of the first electromagnet (21) is set to Pb, and the second pressure sensor (52) detects the pressure of the second chamber in real time. When the pressure of the second chamber is higher than Pb, the proportional valve (2) opens and connects the first chamber and the second chamber. When the pressure of the second chamber is lower than Pb, the proportional valve (2) closes.

9. The control method for a hydraulic system according to claim 7, characterized in that, When the excavator's swing motor rotates clockwise for braking, the second electromagnet (62) of the swing reversing valve (6) is de-energized, the flow of the main pump (70) is cut off, and the motor body (1) tends to rotate clockwise due to inertia. The pressure in the first chamber decreases and becomes a low-pressure chamber, while the pressure in the second chamber increases and becomes a high-pressure chamber. At this time, the starting value of the first electromagnet (21) is set to Pc. The second pressure sensor (52) detects the pressure in the second chamber in real time. When the pressure in the second chamber is higher than Pc, the proportional valve (2) opens and connects the first chamber and the second chamber. When the pressure in the second chamber is lower than Pc, the proportional valve (2) closes. When the excavator's slewing motor rotates counterclockwise for braking, the third electromagnet (63) of the slewing reversing valve (6) is de-energized, the flow of the main pump (70) is cut off, and the motor body (1) tends to rotate counterclockwise due to inertia. The pressure in the second chamber decreases and becomes a low-pressure chamber, while the pressure in the first chamber increases and becomes a high-pressure chamber. At this time, the starting value of the first electromagnet (21) is set to Pd. The first pressure sensor (51) detects the pressure in the first chamber in real time. When the pressure in the first chamber is higher than Pd, the proportional valve (2) opens and connects the first chamber and the second chamber. When the pressure in the first chamber is lower than Pd, the proportional valve (2) closes.

10. The control method for a hydraulic system according to claim 7, characterized in that, When the excavator's rotary motor rotates clockwise to prevent swaying, the motor body (1) tends to rotate counterclockwise due to the braking process. The pressure in the first chamber rises to become a high-pressure chamber, and the pressure in the second chamber drops to become a low-pressure chamber. At this time, the given current value of the first electromagnet (21) is adjusted according to the pressure difference between the first chamber and the second chamber. The first pressure sensor (51) detects the pressure in the first chamber in real time, and the second pressure sensor (52) detects the pressure in the second chamber in real time. The opening of the proportional valve (2) is proportional to the pressure difference between the first chamber and the second chamber. When the excavator's rotary motor rotates counterclockwise to prevent swaying, the motor body (1) tends to rotate clockwise due to the braking process. The pressure in the first chamber decreases to become a low-pressure chamber, and the pressure in the second chamber increases to become a high-pressure chamber. At this time, the given current value of the first electromagnet (21) is adjusted according to the pressure difference between the first chamber and the second chamber. The first pressure sensor (51) detects the pressure in the first chamber in real time, and the second pressure sensor (52) detects the pressure in the second chamber in real time. The opening degree of the proportional valve (2) is proportional to the pressure difference between the first chamber and the second chamber.

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