CN118180351A - Double-servo valve control squeeze casting equipment - Google Patents
Double-servo valve control squeeze casting equipment Download PDFInfo
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- CN118180351A CN118180351A CN202410601696.7A CN202410601696A CN118180351A CN 118180351 A CN118180351 A CN 118180351A CN 202410601696 A CN202410601696 A CN 202410601696A CN 118180351 A CN118180351 A CN 118180351A
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- 238000009716 squeeze casting Methods 0.000 title claims abstract description 19
- 239000003921 oil Substances 0.000 claims abstract description 139
- 238000004512 die casting Methods 0.000 claims abstract description 40
- 238000010009 beating Methods 0.000 claims abstract description 22
- 238000001125 extrusion Methods 0.000 claims abstract description 22
- 239000000463 material Substances 0.000 claims abstract description 18
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 5
- 230000009977 dual effect Effects 0.000 claims description 8
- 238000002955 isolation Methods 0.000 claims description 8
- 238000007599 discharging Methods 0.000 claims description 4
- 238000004146 energy storage Methods 0.000 claims description 3
- 238000009530 blood pressure measurement Methods 0.000 claims 4
- 238000002347 injection Methods 0.000 abstract description 13
- 239000007924 injection Substances 0.000 abstract description 13
- 238000000034 method Methods 0.000 abstract description 11
- 230000008569 process Effects 0.000 abstract description 11
- 238000004519 manufacturing process Methods 0.000 description 10
- 238000010586 diagram Methods 0.000 description 6
- 230000001276 controlling effect Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 4
- 230000007547 defect Effects 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 238000013461 design Methods 0.000 description 3
- 238000005516 engineering process Methods 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 238000005266 casting Methods 0.000 description 2
- 238000005086 pumping Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011217 control strategy Methods 0.000 description 1
- 239000000839 emulsion Substances 0.000 description 1
- 238000000605 extraction Methods 0.000 description 1
- 235000012438 extruded product Nutrition 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000005495 investment casting Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000012797 qualification Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 239000000243 solution Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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Abstract
The invention relates to the field of hydraulic control, and particularly discloses a double-servo valve control squeeze casting device, which comprises: extruding an oil cylinder; a lifting cylinder; swinging the oil cylinder; a quick-discharge hydraulic control module; a hydraulic control module for beating materials; a die casting machine control module; the extrusion oil cylinder is arranged on the upper side of the lifting oil cylinder, the swing oil cylinder is arranged on the lower side of the lifting oil cylinder, the extrusion oil cylinder, the lifting oil cylinder and the swing oil cylinder are communicated through a hydraulic pipeline, hydraulic oil is arranged in the hydraulic pipeline, and the extrusion oil cylinder drives the lifting oil cylinder through hydraulic pressure so as to drive the swing oil cylinder; the extrusion oil cylinder and the swing oil cylinder are communicated with each other and are provided with a material-beating hydraulic control module which is connected with a die casting machine control module; one side of the lifting oil cylinder is connected with a quick-discharge hydraulic control module, the quick-discharge hydraulic control module is connected with a pressurizing hydraulic control module, and high-speed and accurate flow control is realized in the injection process.
Description
Technical Field
The invention relates to the field of hydraulic control systems, in particular to extrusion casting equipment controlled by double servo valves.
Background
The hydraulic control system of the extrusion casting equipment is a hydraulic part for a die casting machine and is mainly responsible for controlling hydraulic parameters in the die casting process so as to ensure the product quality and the production efficiency, and the hydraulic system is a whole set of device which takes oil as a working medium, utilizes the pressure energy of the oil and controls a hydraulic actuating mechanism to work through accessories such as a control valve and the like. The working principle is that the pressure is changed to increase acting force, so that the automatic operation and control of the hydraulic system of various mechanical equipment taking an oil way as a core are realized, and the hydraulic system plays roles of energy transmission and connection of all parts. A complete hydraulic system consists of: a power element: and the device is used for converting mechanical energy into hydraulic energy of oil. The most common form is a hydraulic pump, which supplies pressurized oil to a hydraulic system. The executing element comprises: and an element for converting the hydraulic energy of the oil into mechanical energy. For example, a linear-motion hydraulic cylinder or a rotary-motion hydraulic motor. Control element: and an element for controlling or regulating the pressure, flow or direction of flow of the oil in the system. Different combinations of these elements form hydraulic systems of different functions. Auxiliary element: other elements than the three parts described above, such as a tank, a filter, an oil pipe, etc. They are critical to ensure that the system is functioning properly. Working medium: mainly comprises various hydraulic oil, emulsion and synthetic hydraulic fluid. The hydraulic system uses a working medium for energy and signal transfer. Regardless of the size of the hydraulic equipment and the complexity of the system, any hydraulic system is composed of the five parts. The hydraulic system is widely applied in the fields of industry, machinery, aviation, automobiles and the like, and realizes efficient and accurate power transmission and control.
However, the hydraulic control system of the die casting machine in the prior art has the following technical defects:
The prior art shot speed range is limited to 0.02 to 0.5 meters per second, indicating that the original control system may be inadequate to handle the higher speed requirements in terms of response speed or tuning accuracy. This limits the production efficiency and the possibilities for wider application, especially in high precision casting processes where fast injection is required.
Conventional systems have drawbacks in maintaining stability of the pressure at the outlet, possibly due to the design of the hydraulic control system being inaccurate or the components used (e.g., relief valves and solenoid valves) not being able to work effectively in concert. Such pressure instability can cause the material to shake, thereby affecting the quality and yield of the product.
If the clamping operation is not smooth enough, defects may occur in the product due to vibration or instability. This suggests that prior art control algorithms during closing may not be advanced enough to ensure accurate closing and locking of the mold in high pressure environments, which is critical for high quality die casting products.
Disclosure of Invention
The invention aims to provide a double-servo valve control squeeze casting device for solving the technical problems in the background technology.
Based on the thought, the invention provides the following technical scheme: a dual servo valve controlled squeeze casting apparatus comprising: extruding an oil cylinder; a lifting cylinder; swinging the oil cylinder; a quick-discharge hydraulic control module; a hydraulic control module for beating materials; a die casting machine control module; the extrusion oil cylinder is arranged on the upper side of the lifting oil cylinder, the swing oil cylinder is arranged on the lower side of the lifting oil cylinder, the extrusion oil cylinder, the lifting oil cylinder and the swing oil cylinder are communicated through a hydraulic pipeline, hydraulic oil is arranged in the hydraulic pipeline, and the lifting oil cylinder can drive the swing oil cylinder due to the driving of hydraulic pressure in the extrusion oil cylinder; the extrusion oil cylinder and the swing oil cylinder are communicated with the material beating hydraulic control module, and the material beating hydraulic control module is connected with the die casting machine control module; one side of the lifting oil cylinder is connected with the quick-discharge hydraulic control module, and the quick-discharge hydraulic control module is connected with the hydraulic pressurizing module.
Preferably, the quick drain pressure control module comprises a first overflow valve, a first single piston cylinder, an oil tank, a first pressure relay and a first three-position four-way electromagnetic valve; the first overflow valve is communicated with one side of the lifting oil cylinder through an oil way, an oil tank is communicated with one side of the first overflow valve, the other side of the first overflow valve is communicated with the first pressure relay, the first pressure relay is communicated with the first three-position four-way electromagnetic valve, and the first single-piston cylinder is arranged on an oil way on one side communicated with the oil tank.
Preferably, the bottom of the oil tank returns oil, and an oil way communicated with the oil tank is provided with an adjustable throttle valve; the first three-position four-way electromagnetic valve is connected with a flowmeter.
Preferably, the hydraulic pressurizing module comprises a second pressure relay, a second three-position four-way electromagnetic valve, a first pressure measuring joint, a third pressure relay, a second overflow valve and a third three-position four-way electromagnetic valve; the oil ways at two sides of the second three-position four-way electromagnetic valve are respectively communicated with one side of the swing oil cylinder and the second pressure relay, the second pressure relay is communicated with the other side of the swing oil cylinder, and the second pressure relay is connected with a pressure measuring joint in parallel; the oil circuit of the second pressure relay and the second three-position four-way electromagnetic valve is communicated with the first pressure measuring joint, the oil circuit of the second pressure relay and the second three-position four-way electromagnetic valve is communicated with the oil circuit of the oscillating cylinder and the oil circuit of the second three-position four-way electromagnetic valve is communicated with the third three-position four-way electromagnetic valve, the third three-position four-way electromagnetic valve is respectively communicated with the third pressure relay and the second overflow valve, and the third pressure relay is communicated with the lifting cylinder.
Preferably, the hydraulic control module for material beating further comprises a first electromagnetic valve, a third overflow valve, a second single piston cylinder, a third single piston cylinder, a first two-way four-position motorized valve, a second pressure measuring joint and a third pressure measuring joint, wherein the first electromagnetic valve is communicated with the third four-way electromagnetic valve, an oil way communicated between the first electromagnetic valve and the third four-way electromagnetic valve is provided with the second single piston cylinder, the first electromagnetic valve is connected with the third overflow valve in series, one side of the oil way connected with the third overflow valve in series is connected with the third single piston cylinder, the third single piston cylinder is communicated with the first two-way four-position motorized valve, and the oil way extending from the first two-way four-position motorized valve is provided with the second pressure measuring joint and the third pressure measuring joint which are oppositely arranged.
Preferably, the system further comprises a fourth pressure measuring joint, a fourth pressure relay, a gas isolation type energy accumulator, a first adjustable throttle valve, a second adjustable throttle valve, a filter, a pressure switch, a fifth pressure measuring joint and a sixth pressure measuring joint; the other side of the oil way of the first electromagnetic valve and the third overflow valve which are connected in series is connected with the first adjustable throttle valve, the first adjustable throttle valve is connected in series with the second adjustable throttle valve, the first adjustable throttle valve is communicated with a gas isolation type energy accumulator, the gas isolation type energy accumulator is communicated with the fourth pressure measuring joint and the fourth pressure relay, the oil way extending out of the second adjustable throttle valve is communicated with the filter, the filter is connected in series with the pressure switch, and the oil way extending out of the filter is provided with a fifth pressure measuring joint and a sixth pressure measuring joint which are arranged oppositely.
Preferably, the hydraulic pump further comprises a fourth single piston cylinder, a second two-position four-way motor valve, a seventh pressure measuring joint and an eighth pressure measuring joint; the fourth single piston cylinder is respectively communicated with the third single piston cylinder and the second adjustable throttle valve, the fourth single piston cylinder is also communicated with the second two-position four-way motor valve, and an oil way extending out of the second two-position four-way motor valve is provided with a seventh pressure measuring joint and an eighth pressure measuring joint which are oppositely arranged; the hydraulic control system also comprises a fifth single-piston cylinder, a third adjustable throttle valve, a third two-position four-way motor valve and a fourth two-position four-way motor valve; the fifth single piston cylinder is respectively communicated with the fourth single piston cylinder and the second adjustable throttle valve, the fifth single piston cylinder is connected with the third adjustable throttle valve and the third two-position four-way motor valve in parallel, and an oil way extending out of the fifth single piston cylinder is connected with the fourth two-position four-way motor valve.
Preferably, the hydraulic pump further comprises a sixth single piston cylinder, a fifth two-position four-way motor valve, a ninth pressure measuring joint and a tenth pressure measuring joint; the sixth single piston cylinder is respectively communicated with the fourth two-position four-way motor valve and the fast liquid discharge pressure control module, the sixth single piston cylinder is also communicated with the fifth two-position four-way motor valve, and an oil way extending out of the fifth two-position four-way motor valve is connected with a ninth pressure measuring joint and a tenth pressure measuring joint.
Preferably, the die casting machine control module comprises a die adjusting part, a die locking part, a thimble part, a core drawing part and a driver module; the die adjusting part, the die locking part, the thimble part and the core pulling part are connected through hydraulic valves, and the driver module is connected with the die adjusting part, the die locking part, the thimble part and the core pulling part; the pumping core part is communicated with the third three-position four-way electromagnetic valve, and the driver module is communicated with the pressurizing hydraulic control module.
Compared with the prior art, the invention has the beneficial effects that:
The original shot speed ranges from 0.02 to 0.5 m/s, while the shot speed is raised to 0.02 to 3 m/s by employing a dual servo valve control system. This change is not only an increase in value, but also a fly-through of the mass of the shot velocity. By precisely controlling the operation of the squeeze cylinder and the swing cylinder, the hydraulic system can quickly respond and precisely adjust the velocity, thereby achieving high-speed and precise metal flow control during injection. This control capability is particularly important, especially in handling complex die castings and industrial applications where extremely high precision is required.
By adding a lift quick drain valve control, the system is able to maintain a constant pressure value at the outlet during die casting. The constant pressure control effectively solves the problem of 'beating shake' common in the traditional die casting process. The shot jitter is caused by pressure fluctuations that can lead to defects in the die cast product. The components in the quick-discharge hydraulic control module, such as the overflow valve and the electromagnetic valve, work cooperatively to quickly adjust the pressure and ensure the stable transition of the pressure in the die casting process, thereby greatly improving the qualification rate of products.
The proportional control algorithm allows the die casting machine to achieve smooth operation during the closing process. Smooth closing is critical to ensuring a good quality extruded product, as any vibration or instability during closing can lead to product defects.
The algorithm regulates hydraulic valves (e.g., a third three-position, four-way solenoid valve) and other key components to ensure that pressure and speed are precisely controlled from closed to open during the entire die casting cycle. The accurate control reduces mechanical stress in the production process, optimizes energy use, and further improves production efficiency and product quality.
Drawings
FIG. 1 is a schematic diagram of a main frame of a dual servo valve controlled squeeze casting apparatus of the present invention;
FIG. 2 is a piping diagram of a quick drain hydraulic control module of a dual servo valve controlled squeeze casting apparatus of the present invention;
FIG. 3 is a piping diagram of a hydraulic control module for controlling squeeze casting equipment with a dual servo valve according to the present invention;
FIG. 4 is a circuit diagram of a die casting machine control module of a dual servo valve controlled squeeze casting apparatus of the present invention;
FIG. 5 is a schematic diagram of a prior art fast drain hydraulic system;
fig. 6 is a schematic diagram of the hydraulic system of the prior art.
Detailed Description
Referring to fig. 1, a twin servo valve controlled squeeze casting apparatus comprises: an extrusion cylinder 1; a lift cylinder 2; a swing cylinder 3; a fast liquid discharge pressure control module A; pressurizing the hydraulic control module B; a die casting machine control module C; the extrusion oil cylinder 1 is arranged on the upper side of the lifting oil cylinder 2, the swing oil cylinder 3 is arranged on the lower side of the lifting oil cylinder 2, the extrusion oil cylinder 1, the lifting oil cylinder 2 and the swing oil cylinder 3 are communicated through a hydraulic pipeline, hydraulic oil is arranged in the hydraulic pipeline, and the extrusion oil cylinder 1 drives the lifting oil cylinder 2 through hydraulic pressure so as to drive the swing oil cylinder 3; the extrusion cylinder 1 and the swing cylinder 3 are communicated with a material-beating hydraulic control module B, and the material-beating hydraulic control module B is connected with a die casting machine control module C; one side of the lifting cylinder 2 is connected with a quick-discharge hydraulic control module A, and the quick-discharge hydraulic control module A is connected with a hydraulic control module B.
As shown in fig. 2, specifically, the fast drain pressure control module includes a first relief valve V429, a first single piston cylinder V442, an oil tank V430, a first pressure relay V433, and a first three-position four-way solenoid valve V431; the first overflow valve V429 is communicated with one side of the lifting cylinder 2 through an oil way, one side of the first overflow valve V429 is communicated with the oil tank V430, the other side of the first overflow valve V429 is communicated with the first pressure relay V433, the first pressure relay V433 is communicated with the first three-position four-way electromagnetic valve V431, and the first single-piston cylinder V442 is arranged on an oil way on one side communicated with the oil tank V430.
For example, in fig. 5, in the original fast liquid discharging pressure system, the servo valve control technology is adopted to adjust the opening of the valve port, so as to realize the accurate control of the material beating speed and the material beating back pressure. In order to optimize the balance between cost and performance, the novel quick hydraulic system adopts a simpler control strategy, namely a control mode of combining a common cartridge valve and a pilot switching valve. The new control system is not only simple in construction but also has a high advantage in terms of cost effectiveness.
Specifically, the pilot switching valve in the new quick-discharging device is respectively responsible for controlling the back pressure of the extrusion oil cylinder in the actions such as material beating, lifting, hammer returning and the like through the accurate regulation and control of the back pressure middle position, the parallel channel position and the cross channel position. The control mode ensures smooth discharge of oil in the material beating process, ensures running stability of the material beating piston rod and effectively avoids shaking phenomenon in the running process. In addition, the switching of lifting and hammering-back actions is smooth and steady through the control mechanism, and the operation consistency and the overall reliability of the system are further improved.
By the improvement, the novel rapid hydraulic system is excellent in improving the operation efficiency and reducing the maintenance requirement, meanwhile, the production cost is reduced, and the cost performance of the whole system is improved. The updating of the technology not only optimizes the use of resources, but also improves the running stability and reliability of the equipment, and brings more economic and effective solutions for users.
Specifically, the bottom of the oil tank V430 returns oil, and an oil path communicated with the oil tank V430 is provided with an adjustable throttle valve; the first three-position four-way electromagnetic valve V431 is connected with a flowmeter.
As shown in fig. 3, specifically, the material-beating hydraulic control module B includes a second pressure relay V488, a second three-position four-way solenoid valve V486, a first pressure measuring joint V489, a third pressure relay V483, a second overflow valve V484, and a third three-position four-way solenoid valve V481; the oil ways on two sides of the second three-position four-way electromagnetic valve V486 are respectively communicated with one side of the swinging oil cylinder 3 and the second pressure relay V488, the second pressure relay V488 is communicated with the other side of the swinging oil cylinder 3, and the second pressure relay V488 is connected with a pressure measuring joint in parallel; the oil paths communicating the second pressure relay V488 and the second three-position four-way electromagnetic valve V486 continue to extend and are provided with a first pressure measuring joint V489, the oil paths communicating the second pressure relay V488 and the second three-position four-way electromagnetic valve V486 continue to extend and are combined to be communicated with the third three-position four-way electromagnetic valve V481, the third three-position four-way electromagnetic valve V481 is respectively communicated with the third pressure relay V483 and the second overflow valve V484, and the third pressure relay V483 is communicated with the lifting oil cylinder 2.
Specifically, the material beating hydraulic control module B further includes a first electromagnetic valve V421, a third overflow valve V520, a second single piston cylinder V491, a third single piston cylinder V415, a first two-way four-position motorized valve V480, a second pressure measuring joint V450 and a third pressure measuring joint V451, an oil path communicated between the first electromagnetic valve V421 and the third three-position four-way electromagnetic valve V481 is provided with a second single piston cylinder V491, the first electromagnetic valve V421 is connected with the third overflow valve V520 in series, one side of an oil path connected with the third overflow valve V520 in series is connected with the third single piston cylinder V415, the third single piston cylinder V415 is communicated with the first two-way four-position motorized valve V480, and an oil path extending from the first two-way four-position motorized valve V480 is provided with the second pressure measuring joint V450 and the third pressure measuring joint V451 which are oppositely arranged.
Specifically, the pressure measuring device further comprises a fourth pressure measuring connector V437, a fourth pressure relay V439, a gas isolation type energy accumulator A401, a first adjustable throttle valve V416, a second adjustable throttle valve V417, a filter F508, a pressure switch S508, a fifth pressure measuring connector V406 and a sixth pressure measuring connector V407; the other side of the oil path of the first electromagnetic valve V421 and the third overflow valve V520 which are connected in series is connected with a first adjustable throttle valve V416, the first adjustable throttle valve V416 is connected with a second adjustable throttle valve V417 in series, the first adjustable throttle valve V416 is communicated with a gas isolation type energy accumulator A401, the gas isolation type energy accumulator A401 is communicated with a fourth pressure measuring joint V437 and a fourth pressure relay V439, the oil path extending from the second adjustable throttle valve V417 is communicated with a filter F508, the filter is connected with a pressure switch S508 in series, and the oil path extending from the filter F508 is provided with a fifth pressure measuring joint V406 and a sixth pressure measuring joint V407 which are arranged oppositely.
Specifically, the hydraulic pump further comprises a fourth single piston cylinder V455, a second two-position four-way motorized valve V454, a seventh pressure measuring joint V452 and an eighth pressure measuring joint V453; the fourth single piston cylinder V455 is respectively communicated with the third single piston cylinder V415 and the second adjustable throttle valve V417, the fourth single piston cylinder V455 is also communicated with the second two-position four-way motorized valve V454, and an oil path extending from the second two-position four-way motorized valve V454 is provided with a seventh pressure measuring joint V452 and an eighth pressure measuring joint V453 which are oppositely arranged; the hydraulic control system further comprises a fifth single-piston cylinder V412, a third adjustable throttle valve V490, a third two-position four-way motor valve V411 and a fourth two-position four-way motor valve V428; the fifth single piston cylinder V412 is respectively communicated with the fourth single piston cylinder V455 and the second adjustable throttle valve V417, the fifth single piston cylinder V412 is connected in parallel with the third adjustable throttle valve V490 and the third two-position four-way motorized valve V411, and an oil path extending from the fifth single piston cylinder V412 is connected with the fourth two-position four-way motorized valve V428.
Specifically, the hydraulic pump further comprises a sixth single-piston cylinder V408, a fifth two-position four-way motor valve V403, a ninth pressure measuring joint V409 and a tenth pressure measuring joint V410; the sixth single-piston cylinder V408 is respectively communicated with the fourth two-position four-way motor valve V428 and the quick drain pressure control module A, the sixth single-piston cylinder V408 is also communicated with the fifth two-position four-way motor valve V403, and an oil path extending out of the fifth two-position four-way motor valve V403 is connected with a ninth pressure measuring joint V409 and a tenth pressure measuring joint V410.
For example, in the old hydraulic system, as shown in fig. 6, the stored energy pressure enters the oil cylinder after being controlled by the combination of the cartridge valve and the servo valve, and this configuration causes a large pressure loss, so that the pressure drop of the whole system is large. In comparison, in the new design of the hydraulic system, the energy storage pressure directly enters the oil cylinder through the servo valve, so that the extra pressure loss caused by multi-valve joint control is effectively reduced, and the pressure drop of the system is obviously reduced.
In addition, a set of smaller bore servo valves are used in older systems for meter-in control, which limits shot speed control to the range of 0.02 to 0.5 meters per second, and therefore the range of applicability to shot products is relatively narrow. In contrast, the new hydraulic beating system adopts a large servo valve, a small servo valve and a small servo valve with different diameters to realize finer throttle inlet control. The design expands the control range of the injection speed to 0.02 to 3 meters per second, and greatly expands the adaptability range of injection products. When the injection speed is 0.02 to 0.5 m/s, the system is controlled by a servo valve with a small drift diameter; when the injection speed is required to be adjusted to 0.5 to 3 m/s, the servo valve with large diameter is switched. This arrangement ensures that the control flow rate through the servo valve is maintained within the optimum opening interval of the servo valve port, regardless of the injection speed, achieving the highest efficiency and control accuracy.
The newly added double-servo valve control system further enhances the adjustment range of injection speed, so that a customer can flexibly select proper injection speed according to the production requirement of the customer. The system supports ten-section adjustment of injection speed, and can conveniently realize mode switching from extrusion die casting to common die casting. The flexibility not only improves the convenience of operation, but also optimizes the production flow, so that the die casting process is more diversified, and the accurate die casting requirements of different products and materials are met, thereby improving the efficiency of the whole production line and the quality of the products.
As shown in fig. 4, specifically, the die casting machine control module C includes a die adjusting portion 4, a die locking portion 5, a thimble portion 6, a drawing core portion 7, and a driver module; the die adjusting part 4, the die locking part 5, the thimble part 6 and the core pulling part 7 are connected through hydraulic valves, and the driver module is connected with the die adjusting part 4, the die locking part 5, the thimble part 6 and the core pulling part 7; the pumping core 7 is communicated with a third three-position four-way electromagnetic valve V481, and the driver module is communicated with a pressurizing liquid pressure control module B.
The die adjusting part is mainly responsible for adjusting the position of the die so as to adapt to the die casting requirements of different sizes and shapes. The die adjusting part can accurately move the die through the control of the hydraulic valve, so that the die is ensured to be aligned correctly before die assembly. The function of the mold locking part is to lock the mold during die casting and prevent the mold from being displaced during high-pressure injection. The locking mechanism is usually implemented by a powerful hydraulic or mechanical locking device, ensuring that the die remains closed throughout the die casting cycle, and the ejector pin portion involves the use of ejector pins to eject the molded die casting from the die, which requires precise control of the ejector pin action to prevent damage to the die casting or die. The extraction core is used to create complex internal cavities or depressions in the die casting process. The core puller is typically part of a mold that can be moved back and forth before injection to form the desired product shape. The driver module provides power and control for all of the above. The die-casting device is connected with all parts through hydraulic valves, ensures that all the parts work cooperatively and completes the die-casting task. All hydraulic and mechanical actions can be precisely coordinated through the integrated control module, so that the speed and accuracy of die casting are improved. This is particularly important for producing die castings which are complex or require high precision. The accurate control of the system reduces variability of products in the production process, and ensures that each die casting can meet the quality requirement of high standards. The automated die casting process reduces direct operator intervention, reduces operational complexity, and improves safety of the production process. Through the fine adjustment of the die adjusting part and the core drawing part, the die casting machine can adapt to die casting tasks with various specifications and complexity, provides great flexibility and meets the variable demands of the market.
Claims (9)
1. A twin servo valve controlled squeeze casting apparatus comprising:
An extrusion cylinder (1);
A lift cylinder (2);
A swing cylinder (3);
A quick-drain hydraulic control module (A);
a hydraulic control module (B) for beating materials;
A die casting machine control module (C);
The extrusion oil cylinder (1) is arranged on the upper side of the lifting oil cylinder (2), the swing oil cylinder (3) is arranged on the lower side of the lifting oil cylinder (2), the extrusion oil cylinder (1), the lifting oil cylinder (2) and the swing oil cylinder (3) are communicated through a hydraulic pipeline, hydraulic oil is arranged in the hydraulic pipeline, and the swing oil cylinder (3) can be driven by the driving of hydraulic pressure in the extrusion oil cylinder (1);
The extrusion oil cylinder (1) and the swing oil cylinder (3) are communicated with the material beating hydraulic control module (B), and the material beating hydraulic control module (B) is connected with the die casting machine control module (C);
One side of the lifting oil cylinder (2) is connected with the quick discharging hydraulic control module (A), and the quick discharging hydraulic control module (A) is connected with the material beating hydraulic control module (B).
2. The twin-servo valve controlled squeeze casting equipment according to claim 1, wherein the fast-drain hydraulic control module (a) comprises a first relief valve (V429), a first single-piston cylinder (V442), an oil tank (V430), a first pressure relay (V433) and a first three-position four-way solenoid valve (V431);
The hydraulic lifting device is characterized in that the first overflow valve (V429) is communicated with one side of the lifting oil cylinder (2) through an oil way, an oil tank (V430) is communicated with one side of the first overflow valve (V429), the other side of the first overflow valve (V429) is communicated with the first pressure relay (V433), the first pressure relay (V433) is communicated with the first three-position four-way electromagnetic valve (V431), and the first single-piston cylinder (V442) is arranged on an oil way on one side communicated with the oil tank (V430).
3. The double-servo valve controlled squeeze casting equipment according to claim 2, characterized in that the bottom return oil of the oil tank (V430) is provided with an adjustable throttle in the oil path communicating with the oil tank (V430);
the first three-position four-way electromagnetic valve (V431) is connected with a flowmeter.
4. A twin-servo valve controlled squeeze casting apparatus as defined in claim 3, wherein the knockout hydraulic control module (B) comprises a second pressure relay (V488), a second three-position four-way solenoid valve (V486), a first pressure tap (V489), a third pressure relay (V483), a second overflow valve (V484), a third three-position four-way solenoid valve (V481);
The oil paths on two sides of the second three-position four-way electromagnetic valve (V486) are respectively communicated with one side of the swing oil cylinder (3) and the second pressure relay (V488), the second pressure relay (V488) is communicated with the other side of the swing oil cylinder (3), and the second pressure relay (V488) is connected with a pressure measuring joint in parallel;
The oil circuit of intercommunication second pressure relay (V488) with second three-position four-way solenoid valve (V486) continues to extend and is provided with first pressure measurement joint (V489), intercommunication second pressure relay (V488) with the oil circuit of second three-position four-way solenoid valve (V486) with intercommunication swing hydro-cylinder (3) and the oil circuit of second three-position four-way solenoid valve (V486) continues to extend and merge with third three-position four-way solenoid valve (V481) intercommunication, third three-position four-way solenoid valve (V481) respectively with third pressure relay (V483) with second overflow valve (V484) intercommunication, third pressure relay (V483) intercommunication hoist cylinder (2).
5. The twin-servo valve controlled squeeze casting apparatus of claim 4, wherein the knockout hydraulic control module (B) further comprises a first solenoid valve (V421), a third spill valve (V520), a second single-piston cylinder (V491), a third single-piston cylinder (V415), a first two-way four-position motorized valve (V480), a second pressure tap (V450), and a third pressure tap (V451);
The first electromagnetic valve (V421) is communicated with the third three-position four-way electromagnetic valve (V481), an oil way communicated between the first electromagnetic valve (V421) and the third three-position four-way electromagnetic valve (V481) is provided with the second single-piston cylinder (V491), the first electromagnetic valve (V421) is connected in series with the third overflow valve (V520), one side of an oil way of the first electromagnetic valve (V421) and the third overflow valve (V520) which is connected in series is connected with the third single-piston cylinder (V415), the third single-piston cylinder (V415) is communicated with the first two-way four-position motor valve (V480), and the oil way extending from the first two-way four-position motor valve (V480) is provided with the second pressure measuring joint (V450) and the third pressure measuring joint (V451) which are oppositely arranged.
6. The dual servo valve controlled squeeze casting apparatus of claim 5, further comprising a fourth pressure tap (V437), a fourth pressure relay (V439), a gas isolated accumulator (a 401), a first adjustable throttle valve (V416), a second adjustable throttle valve (V417), a filter (F508), a pressure switch (S508), a fifth pressure tap (V406), and a sixth pressure tap (V407);
The other side of the oil way of first solenoid valve (V421) with third overflow valve (V520) series connection is connected with first adjustable throttle valve (V416), first adjustable throttle valve (V416) series connection second adjustable throttle valve (V417), first adjustable throttle valve (V416) intercommunication gas isolation formula energy storage ware (A401), gas isolation formula energy storage ware (A401) intercommunication fourth pressure measurement joint (V437) and fourth pressure relay (V439), the oil way that second adjustable throttle valve (V417) extends is connected with filter (F508), the filter series connection pressure switch (S508), the oil way that filter (F508) extends is provided with relative setting fifth pressure measurement joint (V406) and sixth pressure measurement joint (V407).
7. The dual servo valve controlled squeeze casting apparatus of claim 6, further comprising a fourth single piston cylinder (V455), a second two-position four-way motorised valve (V454), a seventh pressure tap (V452) and an eighth pressure tap (V453);
The fourth single piston cylinder (V455) is respectively communicated with the third single piston cylinder (V415) and the second adjustable throttle valve (V417), the fourth single piston cylinder (V455) is also communicated with the second two-position four-way motor valve (V454), and an oil path extending from the second two-position four-way motor valve (V454) is provided with the seventh pressure measuring joint (V452) and the eighth pressure measuring joint (V453) which are oppositely arranged;
The hydraulic control system further comprises a fifth single-piston cylinder (V412), a third adjustable throttle valve (V490), a third two-position four-way motor valve (V411) and a fourth two-position four-way motor valve (V428);
The fifth single piston cylinder (V412) is respectively communicated with the fourth single piston cylinder (V455) and the second adjustable throttle valve (V417), the fifth single piston cylinder (V412) is connected with the third adjustable throttle valve (V490) and the third two-position four-way motor valve (V411) in parallel, and an oil way extending from the fifth single piston cylinder (V412) is connected with the fourth two-position four-way motor valve (V428).
8. The twin servo valve controlled squeeze casting apparatus of claim 7, further comprising a sixth single piston cylinder (V408), a fifth two-position four-way motorised valve (V403), a ninth pressure tap (V409) and a tenth pressure tap (V410);
The sixth single-piston cylinder (V408) is respectively communicated with the fourth two-position four-way motor valve (V428) and the quick-discharge hydraulic control module (A), the sixth single-piston cylinder (V408) is also communicated with the fifth two-position four-way motor valve (V403), and an oil way extending out of the fifth two-position four-way motor valve (V403) is connected with a ninth pressure measuring joint (V409) and a tenth pressure measuring joint (V410).
9. The double-servo valve control squeeze casting equipment according to claim 8, wherein the die casting machine control module (C) comprises a die adjusting part (4), a die locking part (5), a thimble part (6), a core pulling part (7) and a driver module;
The die adjusting part (4), the die locking part (5), the thimble part (6) and the core pulling part (7) are connected through a hydraulic valve, and the driver module is connected with the die adjusting part (4), the die locking part (5), the thimble part (6) and the core pulling part (7);
The core pulling part (7) is communicated with the third three-position four-way electromagnetic valve (V481), and the driver module is communicated with the material beating hydraulic control module (B).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410601696.7A CN118180351A (en) | 2024-05-15 | 2024-05-15 | Double-servo valve control squeeze casting equipment |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202410601696.7A CN118180351A (en) | 2024-05-15 | 2024-05-15 | Double-servo valve control squeeze casting equipment |
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| CN118180351A true CN118180351A (en) | 2024-06-14 |
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| CN202410601696.7A Pending CN118180351A (en) | 2024-05-15 | 2024-05-15 | Double-servo valve control squeeze casting equipment |
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Citations (6)
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|---|---|---|---|---|
| JP2011131225A (en) * | 2009-12-24 | 2011-07-07 | Ube Machinery Corporation Ltd | Injection device and injection controlling method of die casting machine |
| CN102672135A (en) * | 2012-05-18 | 2012-09-19 | 苏州三基铸造装备股份有限公司 | Swinging type squeezing system |
| CN108067602A (en) * | 2016-11-15 | 2018-05-25 | 江苏睿阳精密工业股份有限公司 | A kind of injection system of extrusion casting machine |
| CN109277553A (en) * | 2018-10-25 | 2019-01-29 | 广州和德轻量化成型技术有限公司 | Liquid forging machine row material injecting mechanism |
| JP2022091590A (en) * | 2020-12-09 | 2022-06-21 | 東洋機械金属株式会社 | Die-cast machine |
| CN115889731A (en) * | 2023-02-27 | 2023-04-04 | 宁波力劲科技有限公司 | Knockout control method and knockout system of large die casting machine |
-
2024
- 2024-05-15 CN CN202410601696.7A patent/CN118180351A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2011131225A (en) * | 2009-12-24 | 2011-07-07 | Ube Machinery Corporation Ltd | Injection device and injection controlling method of die casting machine |
| CN102672135A (en) * | 2012-05-18 | 2012-09-19 | 苏州三基铸造装备股份有限公司 | Swinging type squeezing system |
| CN108067602A (en) * | 2016-11-15 | 2018-05-25 | 江苏睿阳精密工业股份有限公司 | A kind of injection system of extrusion casting machine |
| CN109277553A (en) * | 2018-10-25 | 2019-01-29 | 广州和德轻量化成型技术有限公司 | Liquid forging machine row material injecting mechanism |
| JP2022091590A (en) * | 2020-12-09 | 2022-06-21 | 東洋機械金属株式会社 | Die-cast machine |
| CN115889731A (en) * | 2023-02-27 | 2023-04-04 | 宁波力劲科技有限公司 | Knockout control method and knockout system of large die casting machine |
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