Slewing control hydraulic system and working machine

Abstract

The utility model belongs to the field of engineering machinery, and discloses a rotation control hydraulic system and an operation machine. The brake oil cylinder is used for braking the motor and comprises a brake cavity connected with a brake oil way; the rotary brake valve is arranged in the brake oil way and comprises an adjustable one-way throttle valve used for controlling the flow speed of oil in the brake oil way. The rotation control hydraulic system can be applied to various operation machines with rotation motors, the oil flow of the braking oil way can be adjusted and controlled, then the braking time is controlled, the problems of stall and shaking of the hydraulic system caused by different working loads during rotation stopping are solved, and the service life of the hydraulic system is prolonged. And the problem of unstable rotation caused in the sudden stop process of rotation is also solved.

Description

Technical Field

[0001] The present application belongs to the field of engineering machinery, and specifically, relates to an operating machine and a rotary control hydraulic system thereof. Background Art

[0002] In operating machinery with a slewing function (such as various cranes, fire trucks, etc.), the slewing mechanism is an important operating mechanism, and its slewing stability directly affects the user experience. In particular, when the slewing stops, due to the large inertia and the inertia that varies with the load size, the stability of the slewing brake is difficult to control accurately. If the brake is too fast, it will cause impact vibration, and if the brake is too slow, the slewing slip will be too large, and the braking time will be increased, which will affect the user experience and may also bring safety hazards or subsequent cumbersome operations. Utility Model Content

[0003] The purpose of the present application is to provide a swing control hydraulic system and a working machine to improve the stability and controllability of swing braking.

[0004] To achieve the above objectives, the present application provides a slewing control hydraulic system, comprising:

[0005] Swing motor;

[0006] A brake oil cylinder, used for motor braking and comprising a brake chamber connected to a brake oil circuit;

[0007] The swing brake valve is arranged in the brake oil circuit and comprises an adjustable one-way throttle valve for controlling the oil flow rate in the brake oil circuit.

[0008] In some embodiments, the adjustable one-way throttle valve is a manual regulating valve with an adjusting hand wheel.

[0009] In some embodiments, the adjustable one-way throttle valve comprises:

[0010] A valve housing, wherein a valve cavity is formed in the housing, and a throttle valve port is formed at a first end of the valve cavity;

[0011] A valve core is arranged close to the throttle valve port;

[0012] A screw rod penetrates from the second end of the valve cavity and elastically presses the valve core toward the throttle valve port;

[0013] The adjusting hand wheel is mounted on the outer end of the screw rod and is used to rotate the screw rod to adjust the opening of the throttle valve port.

[0014] In some embodiments, the adjustable one-way throttle valve comprises:

[0015] A compression spring is arranged between the screw rod and the valve core.

[0016] In some embodiments, the adjustable one-way throttle valve is an electrically controlled one-way throttle valve.

[0017] In some embodiments, the swing control hydraulic system includes a motor brake controller, and the motor brake controller is configured to adjust the opening of the throttle valve port of the adjustable one-way throttle valve according to the load size of the swing motor.

[0018] In some embodiments, the adjustable one-way throttle valve comprises:

[0019] A valve housing, wherein a valve cavity is formed in the housing, and a throttle valve port is formed at a first end of the valve cavity;

[0020] A valve core is disposed near the throttle valve port; and

[0021] The electric push rod penetrates from the second end of the valve cavity and elastically presses the valve core toward the throttle valve port.

[0022] In some embodiments, the swing brake valve is provided with a brake chamber connection port on one side and a brake fluid inlet port and a brake fluid return port on the other side, and the adjustable one-way throttle valve is provided near the brake chamber connection port;

[0023] Wherein, the rotary brake valve comprises an electromagnetic reversing valve and a hydraulically controlled reversing valve, and the adjustable one-way throttle valve, the electromagnetic reversing valve and the hydraulically controlled reversing valve are sequentially arranged in series.

[0024] In some embodiments, the end hydraulic control chamber of the hydraulically controlled reversing valve is connected to the hydraulic control handle through a shuttle valve.

[0025] In addition, the present application also provides a working machine, including the above-mentioned swing control hydraulic system according to the present application.

[0026] In the technical solution of the present application, an adjustable one-way throttle valve is arranged in the brake oil circuit of the brake oil cylinder, so that the oil flow of the brake oil circuit can be adjusted and controlled, and then the braking time can be controlled; by optimizing the swing system and the brake valve, and by matching the closing time of the brake cylinder with the size of the swing inertia, the braking stability of the swing brake valve under various working conditions can be greatly improved. This swing control hydraulic system has low cost, high reliability, strong controllability, and is easy to operate.

[0027] Other features and advantages of the embodiments of the present application will be described in detail in the subsequent detailed description. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The accompanying drawings are used to provide a further understanding of the embodiments of the present application and constitute a part of the specification. Together with the following specific embodiments, they are used to explain the embodiments of the present application, but do not constitute a limitation on the embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without creative work. In the drawings:

[0029] Figure 1 It is a structural schematic diagram of an adjustable one-way throttle valve according to a specific embodiment of the present application;

[0030] Figure 2 It is a hydraulic principle diagram of a swing control hydraulic system according to a specific embodiment of the present application.

[0031] Description of Reference Numerals

[0032] 1 Swing motor 2 Brake cylinder

[0033] 3 Adjustable one-way throttle valve 4 Solenoid reversing valve

[0034] 5 Hydraulic control reversing valve 6 Shuttle valve

[0035] 7 Main valve 8 Guide valve

[0036] 10 Swing brake valve 20 Hydraulic control handle

[0037] 31 Swing brake valve 32 Valve core

[0038] 33 Screw rod 34 Compression spring

[0039] 35 Adjustment hand wheel

[0040] Y Brake chamber connection port P0 Throttle valve port

[0041] P1 Brake fluid inlet

[0042] L0 Brake oil circuit L1 Brake fluid return port DETAILED DESCRIPTION

[0043] The specific implementation of the present application is described in detail below in conjunction with the accompanying drawings. It should be understood that the specific implementation described here is only used to illustrate and explain the present application, and is not used to limit the present application.

[0044] A swing control hydraulic system and a working machine according to the present application will be described below with reference to the accompanying drawings.

[0045] Take a crane as an example. When the boom carrying heavy objects rotates with the slewing mechanism on the crane body, it needs to stop rotating when it reaches a specific position. At this time, the slewing motor driving the slewing mechanism needs to be braked in time. However, in actual operation, the stability of slewing braking is difficult to control accurately. In addition, due to the heavy load and large slewing inertia, braking too quickly will cause impact and vibration. Braking too slowly will cause excessive slewing slippage, poor accuracy of the stop position, and long braking time.

[0046] To this end, the present application discloses a novel slewing control hydraulic system. Figure 2 , a swing control hydraulic system in a specific embodiment may include:

[0047] Rotary motor 1;

[0048] Brake cylinder 2, used for motor braking and including a brake chamber connected to a brake oil circuit L0;

[0049] The swing brake valve 10 is arranged in the brake oil circuit L0 and includes an adjustable one-way throttle valve 3 for controlling the oil flow rate in the brake oil circuit L0.

[0050] The present application aims to achieve the matching of the closing time of the brake cylinder and the size of the rotary inertia through the optimized design of the rotary control hydraulic system and its rotary brake valve, so as to improve the braking stability of the rotary brake valve under various working conditions. To this end, an adjustable one-way throttle valve 3 is set in the brake oil circuit L0. When the load matching of different working conditions is different, the corresponding throttle valve opening is adjusted to control the return oil speed of the brake chamber of the brake cylinder 2, that is, to control the braking force and braking time of the cylinder on the motor, so that each working condition can brake smoothly, thus solving the problem of unstable rotary braking caused by different inertia under different load sizes.

[0051] In the prior art, technicians often strive to adopt more complex detection and control technologies. Although they can bring certain technical effects, they not only increase the number of detection elements and control components, but also require the addition of more buffer elements, such as the use of multiple one-way valves for buffering. Such measures have the defects of high cost, small adjustable range, poor versatility, and weak feasibility. Moreover, for different operating machines and motors of different specifications, it is difficult to ensure the accuracy of various detection elements, pressure shock, and delay problems of the detection and control system at the same time. Of course, there are also relatively simple control methods in the prior art, such as setting a number of one-way dampers in the brake oil circuit to achieve buffering, but because the operating conditions of the operating machinery are complex during actual operation, the load size of each operating condition is different, and the inertia caused is also different. It is difficult for the fixed one-way damper to adapt to various working conditions and make it difficult to make the rotation smooth.

[0052] exist Figure 1 , Figure 2In the embodiment shown, based on the principle of low cost, high reliability and easy operation, a manual regulating valve with an adjusting hand wheel 35 is designed. The operator only needs to operate the adjusting hand wheel 35 to adjust the corresponding throttle valve opening, which is simple and convenient to operate.

[0053] Those skilled in the art will appreciate that the manual regulating valve may have a variety of structural forms. Figure 1 The figure shows a specific structure of a valve body, wherein the adjustable one-way throttle valve 3 comprises:

[0054] A valve housing 31, wherein a valve cavity is formed in the housing, and a throttle valve port P0 is formed at a first end of the valve cavity;

[0055] The valve core 32 is arranged close to the throttle valve port P0;

[0056] The screw 33 penetrates from the second end of the valve cavity and elastically presses the valve core 32 toward the throttle valve port P0;

[0057] The adjusting hand wheel 35 is mounted on the outer end of the screw rod 33 and is used to rotate the screw rod 33 to adjust the opening of the throttle valve port P0.

[0058] like Figure 1 As shown, this throttle valve adopts a cylindrical valve housing, the lower end of the axial valve cavity is connected to the brake fluid inlet P1, and the lower end is also formed with a radial brake cavity connection port Y, and the brake fluid inlet P1 and the brake cavity connection port Y are connected through the throttle valve port P0. Figure 2 That is, the brake fluid inlet port P1 is connected to the brake chamber of the brake cylinder 2 through the throttle valve port P0, and the flow rate of the return oil or the inlet oil of the brake chamber can be adjusted by the opening of the throttle valve port P0. To this end, the valve core 32 arranged near the throttle valve port P0 adopts a conical valve core, which is pushed into the throttle valve port P0 by an external force. The closer to the valve port, the smaller the flow cross-sectional area, until the conical valve core completely abuts against the peripheral wall of the valve port, and the valve port is closed.

[0059] Among them, the screw rod 33 inserted from the top of the valve cavity shown in the figure can be threadedly connected with the upper end of the valve housing 31, so that by rotating the adjusting hand wheel 35, the screw rod 33 can be pushed to move along the axial direction of the valve body, and then the valve core 32 is pushed close to or away from the valve port peripheral wall of the throttle valve port P0. The design of this valve body structure is simple, the power is linearly transmitted, the control of the valve core and the valve port is direct and reliable, the threaded connection and advancement of the screw rod and the valve housing will not cause the problem of stagnation, and the advancement accuracy is controllable and high.

[0060] The screw rod 33 and the valve core 32 can be rigidly connected, but during operation, once the valve core contacts the peripheral wall of the valve port, continuing to rotate the hand wheel can easily damage the valve port structure and reduce the service life of the valve body. For this reason, an elastic member is also provided between the screw rod 33 and the valve core 32, such as the compression spring 34 shown in the figure or other elastic materials, which can serve as a buffer for external forces. At the same time, when a pressurized fluid passes between the brake fluid inlet P1 and the brake chamber connection port Y, it will cause a certain impact on the conical valve core. At this time, the compression spring 34 can also serve as a fluid impact buffer to protect the valve core and increase the service life of the valve core.

[0061] It should be noted that Figure 1 The valve body portion shown is only a part of the manually adjustable one-way throttle valve 3, namely the throttle port portion. The parallel one-way valve portion is well known to those skilled in the art and will not be described or illustrated herein.

[0062] See also Figure 2 Hydraulic schematic diagram, when Figure 1 When the adjusting hand wheel 35 in the control system rotates clockwise, the screw rod 33 reduces the throttling opening of the valve core 32 by compressing the spring 34, thereby reducing the closing time of the brake cylinder. If it rotates counterclockwise, the screw rod 33 moves the valve core 32, which increases the throttling opening of the valve core 32, thereby accelerating the closing time of the brake cylinder. Through the above method, the throttle valve port P0 is always in a suitable position, thereby adjusting the optimal closing time of the brake cylinder and ensuring the smoothness of the rotary system.

[0063] More importantly, the compression spring 34 can be used as a multi-specification replacement part, with different thickness, elastic modulus and other parameters to adapt to different applications, such as different engineering vehicles, motors of different specifications, brake oil pressures of different sizes, etc. As an example, when this manual regulating valve is applied to a rotary control hydraulic system, when the rotary valve is working under different working conditions, the load size corresponding to each adjustment number of the regulating hand wheel 35 can be determined by calculation and verification, so that the user can adjust the load size accordingly according to different load sizes. Figure 1 The number of turns of the adjusting hand wheel 35 in the control system is adjusted to make the motor brake smoothly and the braking time meet the requirements. Therefore, the swing control hydraulic system can include a variety of adjustable one-way throttle valves 3 for replacement, and the specifications of the compression springs 34 in the various adjustable one-way throttle valves 3 are different. In this way, when used for engineering vehicles of different types or specifications, compression springs 34 of different specifications can be selected accordingly.

[0064] In another embodiment, the adjustable one-way throttle valve 3 can be an electrically controlled one-way throttle valve. In this way, there is no need to manually operate the adjusting hand wheel 35, and only the size of the throttle valve opening can be manipulated by electrical control, which has a higher degree of automation.

[0065] In one structural form of the electrically controlled one-way throttle valve, the adjustable one-way throttle valve 3 may include:

[0066] A valve housing 31, wherein a valve cavity is formed in the housing, and a throttle valve port P0 is formed at a first end of the valve cavity;

[0067] A valve core 32 is provided near the throttle valve port P0; and

[0068] The electric push rod penetrates into the second end of the valve cavity and elastically presses the valve core 32 toward the throttle valve port P0.

[0069] It can be seen that electric push rods can replace Figure 1 The screw rod 33 and the adjusting hand wheel 35 in the middle. By controlling the current size of the electric push rod, the linear stroke of the electric push rod can be controlled, that is, the stroke of the control valve core 32, and finally the opening of the throttle valve port can be controlled.

[0070] When an electrically controlled one-way throttle valve is used, the swing control hydraulic system may include a motor brake controller, which is configured to adjust the opening of the throttle port P0 of the adjustable one-way throttle valve 3 according to the load size of the swing motor 1. Therefore, when the swing control hydraulic system is installed on the working machine, the motor brake controller can be debugged to store the current size of the electric push rod corresponding to various load conditions, so that the opening of the throttle port P0 can be automatically controlled by the motor brake controller under various load conditions.

[0071] See also Figure 2 , the rotary motor 1 is controlled by the main valve 7, which has a main oil inlet P2 and an oil return port T. A conduction valve 8 is connected between the working oil circuits at both ends of the rotary motor 1. When the conduction valve 8 is in the cut-off state, the motor works normally. When the conduction valve 8 is in the on state, the two ends of the motor are connected, at this time the main oil inlet P2 does not enter the oil and the main valve 7 is switched to the middle position, which can make the motor idle without power.

[0072] exist Figure 2 In the hydraulic system, the swing brake valve 10 is provided with a brake chamber connection port Y located on one side (the left side of the virtual frame in the figure) and a brake fluid inlet port P1 and a brake fluid return port L1 located on the other side, and the adjustable one-way throttle valve 3 is arranged near the brake chamber connection port Y. Before the motor is started, the brake of the motor needs to be released. At this time, the brake fluid can be controlled to flow into the brake fluid inlet port P1, and then flow through the swing brake valve 10 from the brake chamber connection port Y along the brake oil circuit L0 to the brake chamber of the brake cylinder 2, thereby compressing the spring of the brake cylinder 2, causing the brake rod to retract, releasing the brake of the motor, and the motor can be started smoothly. When the motor needs to brake, the brake oil circuit L0 can be controlled to return oil, and the return oil passes through the brake chamber connection port Y and the throttle port P0 of the adjustable one-way throttle valve 3, and finally returns oil from the brake fluid return port L1. At this time, the compression spring in the brake cylinder 2 is unfolded, pushing the brake rod to extend to abut and brake the motor.

[0073] To facilitate the switch control of the swing brake valve 10, as an example, Figure 2 The swing brake valve 10 shown may also include an electromagnetic reversing valve 4 and a hydraulically controlled reversing valve 5, and the adjustable one-way throttle valve 3, the electromagnetic reversing valve 4 and the hydraulically controlled reversing valve 5 are sequentially arranged in series. In this way, electric and hydraulic two-stage control can be realized, and the swing brake valve 10 can be controlled by both electric control and hydraulic control to cut off or conduct the brake oil circuit L0, thereby realizing reliable control and redundant control of the swing brake valve 10 and ensuring the oil inlet and return control of the brake oil circuit L0.

[0074] When the hydraulic control method is adopted, the end hydraulic control chamber of the hydraulic control reversing valve 5 can be connected to the hydraulic control handle 20 through the shuttle valve 6. As long as the hydraulic control handle 20 is in motion, that is, in a non-neutral position, the pilot oil output from the a port or b port of the handle will enter the end hydraulic control chamber of the hydraulic control reversing valve 5, so that the brake fluid inlet P1 is connected to the brake oil circuit L0, and the brake oil enters the brake cylinder 2, and the motor brake can be released. When the hydraulic control handle 20 is kept in the neutral position, there is no pressure oil in the end hydraulic control chamber of the hydraulic control reversing valve 5, the hydraulic control reversing valve 5 is switched to the lower valve position, the brake oil circuit L0 is connected to the brake fluid return port L1 to return oil, and the brake cylinder 2 brakes the motor.

[0075] Specifically, when the motor needs to be braked, the motor brake controller can be configured to control the main oil inlet P2 to stop the oil inlet, the main valve 7 is switched to the middle position, and the conduction valve 8 is turned on. At this time, the brake oil circuit L0 is controlled to return oil, that is, the electromagnet Y10 of the electromagnetic reversing valve 4 is not energized, the hydraulic control handle 20 returns to the middle position, the a port or b port of the handle is unloaded, and the hydraulic control reversing valve 5 is switched to the lower valve position under the action of the lower end spring force. The brake oil in the brake chamber of the brake oil cylinder 2 (that is, the rod chamber shown in the figure) passes through the brake oil circuit L0, the brake chamber connection port Y, the throttle valve port P0 of the adjustable one-way throttle valve 3, the electromagnetic reversing valve 4, and the hydraulic control reversing valve 5 in sequence, and finally returns oil and unloads from the brake fluid return port L1. At this time, the brake rod of the brake oil cylinder 2 is reset by the spring force, locking the rotary motor 1.

[0076] However, in actual work, the motor load size will vary with different working conditions. The greater the load, the greater the inertia. At this time, if the brake cylinder is closed too quickly, it will cause the rotary system to shake. If it is closed too slowly, the slippage will increase, affecting the user experience and the life of the mechanism. Therefore, the matching relationship between the brake cylinder closing time and the motor load size is particularly important. This application designs an adjustable one-way throttle valve, calculates the matching of the number of adjustment circles of the adjustable one-way valve and the load size of different working conditions, and matches different throttling openings with different working condition loads, so that each working condition can brake smoothly, solving the problem of unstable rotary braking caused by different inertia under different load sizes.

[0077] The slewing control hydraulic system of the present application can be applied to various types of working machines with a slewing motor 1, such as various types of cranes with a slewing mechanism and a telescopic boom, fire trucks, etc. The present application solves the stall and shaking problems of the hydraulic system caused by different workloads when the slewing stops, and also solves the problem of unstable slewing caused during the slewing emergency stop process.

[0078] It should be explained that the rotary control hydraulic system of the present application is not limited to being applied to working machinery, but can also be any other operating system with rotary motion. Figure 1 The manual adjustment method shown can also be an electronic control adjustment method, and the adjustable one-way throttle valve 3 is not limited to Figure 1 The structural form shown may also be other structural forms having this function.

[0079] In the description of the present application, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of the features. In the description of the present application, "plurality" means at least two, such as two, three, etc., unless otherwise clearly and specifically defined.

[0080] In this application, unless otherwise clearly specified and limited, the terms "installed", "connected", "connected", "fixed" and the like should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection, an electrical connection, or communication with each other; it can be a direct connection, or an indirect connection through an intermediate medium, it can be the internal connection of two elements or the interaction relationship between two elements, unless otherwise clearly defined. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood according to specific circumstances.

[0081] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art may combine and combine the different embodiments or examples described in this specification and the features of the different embodiments or examples, without contradiction.

Claims

1. The slewing control hydraulic system is characterized by: The slewing control hydraulic system comprises: Rotary motor (1); A brake oil cylinder (2), used for motor braking and comprising a brake chamber connected to a brake oil circuit (L0); A swing brake valve (10) is arranged in the brake oil circuit (L0) and comprises an adjustable one-way throttle valve (3) for controlling the oil flow rate in the brake oil circuit (L0).

2. The swing control hydraulic system according to claim 1, characterized in that: The adjustable one-way throttle valve (3) is a manual regulating valve with an adjusting hand wheel (35).

3. The swing control hydraulic system according to claim 2, characterized in that: The adjustable one-way throttle valve (3) comprises: A valve housing (31) having a valve cavity formed therein, wherein a throttle valve port (P0) is formed at a first end of the valve cavity; A valve core (32) is arranged close to the throttle valve port (P0); A screw (33) penetrates from the second end of the valve cavity and elastically presses the valve core (32) toward the throttle valve port (P0); The adjusting hand wheel (35) is mounted on the outer end of the screw rod (33) and is used to rotate the screw rod (33) to adjust the opening of the throttle valve port (P0).

4. The swing control hydraulic system according to claim 3, characterized in that: The adjustable one-way throttle valve (3) comprises: A compression spring (34) is arranged between the screw rod (33) and the valve core (32).

5. The swing control hydraulic system according to claim 1, characterized in that: The adjustable one-way throttle valve (3) is an electrically controlled one-way throttle valve.

6. The swing control hydraulic system according to claim 5, characterized in that: The swing control hydraulic system comprises a motor brake controller, which is configured to adjust the opening of the throttle valve port (P0) of the adjustable one-way throttle valve (3) according to the load size of the swing motor (1).

7. The swing control hydraulic system according to claim 5, characterized in that: The adjustable one-way throttle valve (3) comprises: A valve housing (31) having a valve cavity formed therein, wherein a throttle valve port (P0) is formed at a first end of the valve cavity; A valve core (32) is disposed near the throttle valve port (P0); and An electric push rod penetrates from the second end of the valve cavity and elastically presses the valve core (32) toward the throttle valve port (P0).

8. The swing control hydraulic system according to any one of claims 1 to 7, characterized in that: The swing brake valve (10) is provided with a brake chamber connection port (Y) on one side and a brake fluid inlet port (P1) and a brake fluid return port (L1) on the other side, and the adjustable one-way throttle valve (3) is arranged close to the brake chamber connection port (Y); The rotary brake valve (10) comprises an electromagnetic reversing valve (4) and a hydraulically controlled reversing valve (5), and the adjustable one-way throttle valve (3), the electromagnetic reversing valve (4) and the hydraulically controlled reversing valve (5) are sequentially arranged in series.

9. The swing control hydraulic system according to claim 8, characterized in that: The end hydraulic control chamber of the hydraulic control reversing valve (5) is connected to the hydraulic control handle (20) via a shuttle valve (6).

10. An operating machine, characterized in that: The working machine includes the swing control hydraulic system according to any one of claims 1 to 9.

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