Wood splitting machine

Abstract

The log splitter comprises a rack, the rack is connected with an oil tank, tires are installed on the two sides of the oil tank, and the other end of the rack is connected with a foot support; an engine and a gear pump are further mounted on the oil tank; a working beam is arranged on the machine frame, a tail plate and a baffle are installed on the working beam, a blocking piece is arranged between the tail plate and the baffle, a hydraulic cylinder is installed between the tail plate and the blocking piece, the end portion of a piston rod of the hydraulic cylinder is connected with the knife back of the chopper, brackets are installed between the blocking piece and the baffle, the brackets are installed on the two sides of the working beam, and a sliding block is connected to the working beam in a sliding mode. The bottom of the chopper is fixed on the sliding block, and the blade faces the baffle. By utilizing the wood splitting machine designed by the invention, the problems that the cleaning work of the worktable cannot be carried out after each wood splitting action, the speed of the wood splitting action cannot be improved, and various problems can be caused only by simply increasing the power, so that the working efficiency is influenced, even the abrasion of movable parts is aggravated, and the working efficiency is influenced can be solved. And the service life of the log splitter is seriously influenced.

Description

Technical Field

[0001] The invention relates to the technical field of mechanical manufacturing, in particular to a wood splitter. Background Art

[0002] A wood splitter is a mechanical device specifically designed to split logs or large pieces of wood into smaller pieces. The process is as follows: first, the wood is placed on a workbench, then the machine is started. The blades are then pushed forward at high speed or hydraulically squeezed to split the wood along the grain, ultimately completing the splitting process. We typically consider the entire process of splitting the wood from the blades' high-speed push or hydraulic squeezing to the final completion of the splitting process to be one splitting operation. In the prior art, one splitting operation takes 12-15 seconds. This is because after each splitting operation, a large amount of sawdust and debris is inevitably left on the workbench. Furthermore, there is no way to clean the workbench after each splitting operation in the prior art, so the speed of the splitting operation cannot be increased in the prior art. Simply increasing the power can lead to various problems, such as the blades getting stuck and unable to return to their original position, or the wood having an uneven cross-section after splitting. These problems, in turn, affect work efficiency and even increase wear on the moving parts, seriously affecting the service life of the wood splitter itself.

[0003] Therefore, the existing technology has defects and needs to be improved and developed. Summary of the Invention

[0004] The present invention provides a wood splitter that solves the problem in the prior art that, after each wood splitting operation, a large amount of wood chips and residue are inevitably left on the workbench. Furthermore, there is no way to quickly and automatically clean the workbench after each wood splitting operation, thus preventing the prior art from increasing the speed of the wood splitting operation. Simply increasing the power would result in increased wear of the moving parts, seriously shortening the service life of the wood splitter itself.

[0005] An embodiment of the present invention provides a wood splitter, comprising a frame, one end of the frame is connected to a fuel tank, tires are installed on both sides of the fuel tank, and the other end of the frame is connected to a foot support.

[0006] An engine and a gear pump are installed outside the oil tank, the output shaft of the engine is drivingly connected to the drive shaft of the gear pump, and the oil suction port of the gear pump is connected to the oil tank;

[0007] The frame is provided with a working beam, comprising a first flat beam, a second flat beam, and a main beam. The first flat beam and the second flat beam are parallel to each other, the main beam is welded between the first flat beam and the second flat beam, and the second flat beam is connected to the frame by bolts. A tail plate that is upwardly tilted from the first flat beam is welded to one end of the working beam close to the foot support, and a baffle that is higher than the top surface of the first flat beam is welded to the other end of the working beam.

[0008] The bottom of the hydraulic cylinder is connected to the tail plate via bolts, and the piston end of the hydraulic cylinder is detachably connected to the blade back of the cleaver; the blade back of the cleaver is provided with side air deflectors extending to the edges of both sides of the cleaver; the chamber of the hydraulic cylinder is connected to the output interface of the reversing valve via a hose, the oil inlet of the reversing valve is connected to the gear pump via a hose, and the oil return port of the reversing valve is connected to the oil tank via a hose;

[0009] A slider is slidably connected to the first flat beam, and the blade of the cleaver is fixed on the slider;

[0010] A bracket is installed between the hydraulic cylinder and the baffle, and the bracket is used to receive the wood when the wood is being chopped.

[0011] Furthermore, the side air guide plates are arranged on both sides of the riving knife to form a guide curved surface, the guide curved surface is 5 to 6 cm close to the blade of the riving knife, the guide curved surface and the surface of the riving knife facing away from the blade have a backward inclination angle of 15° to 25°, the curvature of the guide curved surface at the end away from the working beam is greater than the curvature of the guide curved surface at the end close to the working beam, and the guide curved surface has a radial involute-like distribution from the end away from the working beam to the end close to the working beam.

[0012] Furthermore, a stopper is detachably connected to the first flat beam, and a slider is slidably connected to the first flat beam, and the bottom of the chopper is fixed on the slider; the stopper is provided with an opening recessed on the upper surface of the first flat beam on the side facing the baffle, and when the slider slides between the opening and the baffle, the stopper is used to limit the distance that the slider slides toward the tail plate.

[0013] Furthermore, there are two brackets, each located on both sides of the first flat beam, and the base of each bracket is connected to the main beam by bolts; the vertical height of the end of the bracket close to the first flat beam from the first flat beam is defined as H, and the vertical height of the top of the slider from the first flat beam is defined as h, H>h, where H and h are positive numbers greater than 0.

[0014] Furthermore, the bracket is defined as a receiving surface for receiving wood, and an opening penetrating the receiving surface is provided on the receiving surface.

[0015] Furthermore, a female flange is installed on the outer wall of the oil tank, the female flange is connected to a male flange, and an interface connecting the inside and outside of the oil tank is installed on the male flange. The end of the hose for connecting the reversing valve and the oil tank is air-tightly connected to the interface, and one end of the interface located inside the oil tank is threadedly connected to an oil return filter.

[0016] Furthermore, reinforcing ribs are welded on the main beam, the top of the reinforcing ribs are welded to the bottom surface of the first flat beam, the bottom of the reinforcing ribs are welded to the top surface of the second flat beam, and the base of the bracket is connected to the reinforcing ribs by bolts.

[0017] Furthermore, the surface of the baffle for receiving the wood is defined as a blocking surface, and a wedge-shaped block is protruding outwardly from the blocking surface.

[0018] Furthermore, the slider includes a first plate, a second plate and a third plate, the chopping knife is fixed on the top surface of the first plate, the first plate is parallel to the third plate, there are two second plates and both are clamped between the first plate and the third plate, the thickness of the second plate is greater than the thickness of the first flat beam, the first flat beam is clamped between the two second plates, the top surface of the second plate is flush with the top surface of the first flat beam, and the distance between the two second plates is greater than the width of the first flat beam.

[0019] Furthermore, when the oil inlet of the reversing valve is connected to the gear pump through a hose, the diameter of the interface of the gear pump is the calculated diameter, and the calculation method includes:

[0020] Step 1: Calculate the theoretical lossless speed;

[0021] Without considering pipeline losses, the theoretical extension speed v0 of the piston is:

[0022]

[0023] Among them, Q p Refers to the rated flow of the gear pump;

[0024] A c Refers to the cross-sectional area of ​​the hydraulic cylinder piston;

[0025] The corresponding one-way time t0 is:

[0026]

[0027] Among them, L s Refers to the rated flow of the gear pump;

[0028] Step 2: Calculate the loss along the hose;

[0029] Calculate the pressure loss Δp of the fluid along the hose using the Darcy-Weisbach formula loss :

[0030]

[0031] Among them, L h Refers to the length of the hose connecting the oil inlet of the reversing valve and the gear pump;

[0032] D1 refers to the inner diameter of the hose connecting the oil inlet of the reversing valve and the gear pump;

[0033] ρ refers to the density of hydraulic oil;

[0034] v h Refers to the volume of the hose connecting the oil inlet of the reversing valve and the gear pump;

[0035] A h Refers to the cross-sectional area of ​​the hose connecting the oil inlet of the reversing valve and the gear pump;

[0036] λ refers to the friction coefficient corresponding to the Reynolds number of the hose, and its value is 0.025;

[0037] Will Substituting,

[0038]

[0039] This formula shows that the smaller the pipe diameter D is, the more rapidly the loss increases;

[0040] Step 3: Calculate the lossy speed and one-way time;

[0041] The effective pressure P that can actually be used for the piston eff for

[0042] P eff =P max -Δp loss ,

[0043] Among them, P max Refers to the maximum pressure of the hydraulic cylinder;

[0044] The corresponding flow attenuation Q eff Can be roughly regarded as

[0045]

[0046] So the actual piston speed v1

[0047]

[0048] Corresponding one-way time t move (D)

[0049]

[0050] Step 4: Calculate the hose filling time;

[0051] At the beginning of each cycle, fresh oil in the hose is pumped into the hose. The pumping time is t fill (D)

[0052]

[0053] This means that the larger the pipe diameter D, the larger the volume and the longer the filling time;

[0054] Step 5: Calculate the total cycle time model;

[0055] Considering the extension and return as two identical single strokes, the effect of the return oil port size on the return speed can be ignored for simplicity. The total time T(D) for a single cycle is:

[0056] T(D)≈2[t fill (D)+t move (D)],

[0057] Substituting into the above formula, we can get

[0058]

[0059] in is a constant;

[0060] Step 6: Calculate the optimal pipe diameter D opt ;

[0061] For the total time of a single cycle T(D), let

[0062]

[0063] Obtain the optimal pipe diameter.

[0064] Beneficial effects:

[0065] As can be seen from the above technical solutions, the present invention provides a wood splitter that reduces the time for each wood splitting operation from the conventional 12-15 seconds to 6-8 seconds. Each time the wood splitting operation is performed, the airflow generated by the high-speed movement of the splitter itself is used to efficiently blow away the wood chips and residues on the surface of the working beam, thereby reducing the damage to the surface of the splitter caused by these residues. Since the power of the splitter involved in the present invention varies greatly during operation, a fixing method using tires and foot supports is adopted to fully utilize the characteristics of the tires to alleviate the kinetic energy impact during operation. Similarly, the strength of the working beam of the present invention is also stronger and more reliable than that of the prior art. These structures ensure that high-speed wood splitting is feasible.

[0066] The overall concept of the present invention breaks with conventional technical approaches. Numerous prior art solutions, such as those for environmental protection equipment, utilize air-guide wings for cleaning. However, conventional considerations in this field suggest that since each wood splitting operation generates debris and shavings, air-guide wings alone cannot remove all of them. Furthermore, the addition of air-guide wings not only increases equipment cost but also wind resistance, making this a relatively inferior solution. However, through the structural design of the present invention, the applicant discovered that by adjusting the diameter of the reversing valve's oil inlet for the hose connecting to the gear pump, the output strength can be increased, thereby accelerating the splitter's operating speed. This faster operating speed, combined with the air-guide wings, effectively removes debris and shavings. Using the technical solution described in the present invention, the rate of debris and shavings removed from the wood splitter blade's trajectory reached 92%, with the rate of debris and shavings with a radius greater than 0.5 mm, which could affect blade movement, being blown away approaching 100%. Moreover, since the time required to complete the wood splitting action is shortened, even though the power consumption of the engine is increased, the energy consumption per unit of wood splitting is reduced.

[0067] By calculating the diameter of the reversing valve's oil inlet for the hose connecting to the gear pump, the efficiency of the splitting cycle is significantly improved. By scientifically calculating the diameters of the reversing valve's oil inlet and the gear pump's connection, the optimal diameter is selected, achieving an optimal balance between hydraulic oil flow resistance in the system and pipe filling speed. This minimizes the filling and movement time of the hydraulic cylinder, minimizing the time required for each complete splitting cycle of the wood splitter and improving overall operating efficiency. Energy consumption is reduced and the burden on the hydraulic system is alleviated. If the diameter is too small, flow resistance increases and pressure loss increases, forcing the gear pump and engine to operate under high load for extended periods, resulting in increased energy consumption and heat generation. If the diameter is too large, the fluid flow rate decreases, slowing system response and causing unnecessary energy loss. By optimizing the diameter, the system operates at the appropriate flow rate and pressure, significantly reducing energy consumption and extending system life. Ensure the stability and reliability of the hydraulic system: When the calibers are properly matched, hydraulic shock is reduced, pipeline vibration is reduced, and the hydraulic oil temperature rises slowly, which helps maintain oil viscosity and lubrication properties, thereby extending the life of core components such as hydraulic cylinders, reversing valves, and gear pumps, and improving the overall reliability and safety of the wood splitter. Reduce repair frequency and maintenance costs: Due to the small fluid shock, light component wear, and reduced equipment failure rate, the number of subsequent maintenance and the frequency of parts replacement are also greatly reduced, thus saving a lot of maintenance costs. The wood splitter's movements during the splitting process are smooth and coherent, with sufficient power, and no jamming or delays. The operator has a good user experience, and production efficiency and work comfort have been significantly improved.

[0068] It should be appreciated that all combinations of the foregoing concepts, as well as additional concepts described in greater detail below, to the extent such concepts are not mutually inconsistent, can be considered to be part of the inventive subject matter of this disclosure.

[0069] The foregoing and other aspects, embodiments, and features of the present invention will be more fully understood from the following description in conjunction with the accompanying drawings. Other additional aspects of the present invention, such as features and / or beneficial effects of the exemplary embodiments, will become apparent from the following description or through practice of specific embodiments according to the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0070] The accompanying drawings are not drawn to scale. In the accompanying drawings, each identical or nearly identical component shown in various figures may be represented by the same reference numeral. For clarity, not every component is labeled in every figure. Embodiments of various aspects of the present invention will now be described by way of example with reference to the accompanying drawings, in which:

[0071] Figure 1 This is a stereoscopic view of a wood splitter in an embodiment of the present application from a first viewing angle.

[0072] Figure 2 This is a stereoscopic view of a wood splitter in an embodiment of the present application from a second viewing angle.

[0073] Figure 3 A wood splitter in the embodiment of the present application Figure 1 Magnified view of point A in .

[0074] Figure 4 This is a schematic structural diagram of a wood splitter blade in an embodiment of the present application.

[0075] Description of Figure Numbers:

[0076] 1. Frame; 2. Fuel tank; 3. Tire; 4. Kickstand; 5. Engine; 6. Gear pump; 7. First flat beam; 8. Second flat beam; 9. Main beam; 10. Tail plate; 11. Baffle; 12. Hydraulic cylinder; 13. Cutter; 14. Reversing valve; 15. Baffle; 16. Bracket; 17. Safety chain; 18. Handle; 19. Reinforcement rib; 20. First flat plate; 21. Second flat plate; 22. Third flat plate. DETAILED DESCRIPTION

[0077] In order to make the purpose, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings of the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the described embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention. Unless otherwise defined, the technical terms or scientific terms used herein should be the common meanings understood by people with ordinary skills in the field to which the present invention belongs.

[0078] The words “first”, “second” and similar words used in the patent application specification and claims of the present invention do not indicate any order, quantity or importance, but are only used to distinguish different components. Similarly, unless the context clearly indicates otherwise, the singular forms of “a”, “an” or “the” and similar words do not indicate a quantity limitation, but rather indicate the presence of at least one. Words such as “include” or “comprise” mean that the elements or objects appearing before “include” or “comprises” cover the features, wholes, steps, operations, elements and / or components listed after “include” or “comprises”, and do not exclude the existence or addition of one or more other features, wholes, steps, operations, elements, components and / or their collections. “Up”, “down”, “left”, “right” and the like are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0079] In the prior art, a large amount of wood chips and residues will inevitably be left on the workbench after each wood splitting action, and there is no way to clean the workbench after each wood splitting action in the prior art. Therefore, the speed of the wood splitting action cannot be increased in the prior art. If the power is simply increased, the wear of the moving parts will be aggravated, which will seriously affect the service life of the wood splitter itself.

[0080] In view of this, the embodiment of the present invention provides a wood splitter, referring to Figures 1 to 3 , including a frame 1, one end of the frame 1 is connected to a fuel tank 2, tires 3 are installed on both sides of the fuel tank 2, the rolling direction of the tires 3 is the same as the length direction of the frame 1, and the other end of the frame 1 is connected to a foot support 4.

[0081] An engine 5 and a gear pump 6 are mounted outside the fuel tank 2. The engine 5's output shaft is drive-connected to the gear pump 6's drive shaft, and the gear pump 6's oil intake is connected to the fuel tank 2. The frame 1 serves as the overall structure of the device, with the fuel tank 2 fixedly mounted on one end. The fuel tank 2 is supported by a support platform extending from its outer wall. In some embodiments, the outer wall of the fuel tank 2 facing the leg support 4 includes a support platform. The engine 5 is bolted to the support platform, and the gear pump 6 is connected to the engine 5's mounting flange via a coupling. The engine 5's output shaft is drive-connected to the gear pump 6's drive shaft, enabling the engine 5 to drive the gear pump 6. Tires 3 are mounted on either side of the fuel tank 2 to facilitate movement and positioning of the wood splitter. The other end is connected to the leg support 4, providing the necessary support and stability for the entire frame 1. Leveraging the rigidity of the frame 1 and the load-bearing capacity of the fuel tank 2 platform, the fuel tank 2, engine 5, and gear pump 6 are tightly integrated, reducing the risk of mechanical loosening caused by a dispersed structure. Engine 5 and gear pump 6 form the core power source for hydraulic oil delivery. The output shaft of engine 5 is directly connected to the drive shaft of gear pump 6 to achieve energy transfer. Gear pump 6 draws hydraulic oil from fuel tank 2 to provide the system pressure required for wood splitting. The hydraulic oil is then distributed by reversing valve 14 and enters the various chambers of hydraulic cylinder 12. The tight integration of fuel tank 2, engine 5, and gear pump 6 clarifies the power transmission path, ensuring tightness and stability during oil delivery and improving response speed.

[0082] Reference Figure 4 There are two side air guide plates, which are arranged on both sides of the riving knife 13 to form two guide surfaces. The end of each guide surface close to the riving knife 13 is 5 to 6 cm away from the blade of the riving knife 13. The guide surface and the surface of the riving knife 13 facing away from the cutting edge are tilted back at an angle of 15° to 25°. The curvature of the guide surface at the end away from the working beam is greater than the curvature of the guide surface at the end close to the working beam. The guide surface is distributed radially involute-like from the end away from the working beam to the end close to the working beam to avoid dynamic imbalance.

[0083] The side of the side air deflector facing away from the cutting edge of the splitting blade 13, i.e., the blade back, can be welded or integrally formed with the splitting blade 13 to form a curved guide surface. This guide surface accelerates and guides the airflow. The air source channel is formed by the airflow being guided by the guide surface to cover areas where wood chips may be scattered after the blade breaks through the wind at high speed. When the blade moves forward at high speed, the guide surface pushes the airflow to the lower end of the guide surface. As the blade moves forward, the airflow below the guide surface lags and covers the work surface during the splitting process, blowing and cleaning it. At the same time, a low-pressure area is formed between the guide surface and the work surface. External air is drawn into the low-pressure area, forming a spiral path that accelerates the rotation, ultimately forming a composite airflow with tangential rotation, and large wood chips are entrained and thrown away by the whirlwind. Furthermore, the airflow forms a protective layer on the blade surface to prevent debris from adhering.

[0084] A working beam is provided on the frame 1, which includes a first flat beam 7, a second flat beam 8 and a main beam 9. The first flat beam 7 and the second flat beam 8 are parallel to each other. The main beam 9 is welded between the first flat beam 7 and the second flat beam 8 and is perpendicular to the first flat beam 7. The second flat beam 8 is connected to the frame 1 by bolts; a tail plate 10 that is upturned on the first flat beam 7 is welded to one end of the working beam close to the foot support 4, and a baffle 11 that is higher than the top surface of the first flat beam 7 is welded to the other end of the working beam.

[0085] The working beam utilizes a modular structure, comprising a first flat beam 7, a second flat beam 8, and a main beam 9. The first and second flat beams 7 and 8 are arranged parallel to each other, with the main beam 9 welded between them to form a single, integral load-bearing platform. An upturned tail plate 10 is welded to one end of the working beam, near the foot support 4, providing a reference and guide for the bottom installation of the hydraulic cylinder 12. A baffle 11, rising above the top surface of the first flat beam 7, is welded to the other end to support or guide the wood during operation. This modular structure, with its multiple layers working together, not only provides high load-bearing rigidity but also provides precise positioning and fixed support for the installation of subsequent components, such as the hydraulic cylinder 12 and the splitting blade 13.

[0086] The bottom of the hydraulic cylinder 12 is connected to the tail plate 10 by bolts, and the piston end of the hydraulic cylinder 12 is detachably connected to the blade back of the riving knife 13; the chamber of the hydraulic cylinder 12 is connected to the output interface of the reversing valve 14 through a hose, the oil inlet of the reversing valve 14 is connected to the gear pump 6 through a hose, and the oil return port of the reversing valve 14 is connected to the oil tank 2 through a hose.

[0087] In some other embodiments, a back plate is welded to the back of the riving blade 13, and a Y-shaped frame is welded to the side of the back plate facing the tailgate 10. The top of the Y-shaped frame is a U-shaped groove, and a screw facing the tailgate 10 is fixed to the center of the groove. Threaded holes are provided on the left and right walls of the U-shaped groove. The piston end of the hydraulic cylinder 12 is threadedly connected to the screws, and additional screws can be used to sequentially connect the left wall of the U-shaped groove, the piston end, and the right wall of the U-shaped groove to secure the piston end, thereby limiting the piston end's travel and protecting the hydraulic cylinder 12. The hydraulic cylinder 12 is mounted on the tailgate 10 and secured by bolts connected to the tailgate 10. Its piston end is directly connected to the back of the riving blade 13, and the blade of the riving blade 13 faces the baffle 11. The oil-holding chamber of hydraulic cylinder 12 is connected to the output port of reversing valve 14 via a flexible hose. This allows oil to enter the chamber of hydraulic cylinder 12 according to the working requirements, causing the piston to move forward, pushing blade 13 to chop the wood. When the oil leaves the chamber of hydraulic cylinder 12 and returns to reversing valve 14, the piston moves backward, bringing blade 13 back with it. This structure utilizes the principles of hydraulic transmission to achieve a smooth conversion of mechanical force, ensuring that blade 13 moves along a predetermined trajectory when driven by hydraulic oil, thereby achieving the desired chopping function. Reversing valve 14 also has an oil return port, which returns oil from hydraulic cylinder 12 to tank 2 through a return oil pipe, completing a closed cycle.

[0088] A removable stopper 15 is attached to the first flat beam 7. A slider is slidably connected to the first flat beam 7, and the bottom of the riving knife 13 is fixed to the slider. The stopper 15 has an opening on the side facing the baffle 11, which is recessed into the upper surface of the first flat beam 7. When the slider slides between the opening and the baffle 11, the stopper 15 limits the distance the slider can slide toward the tailgate 10. The recessed opening in the upper surface of the first flat beam 7 means that, while the upper surface of the first flat beam 7 remains unchanged, the bottom of the stopper 15 on the side facing the baffle 11 is recessed toward the tailgate 10, forming an opening with the upper surface of the first flat beam 7.

[0089] A bracket 16 is installed between the baffle 15 and the baffle 11. There are two brackets 16, which are located on both sides of the first flat beam 7. The base of each bracket 16 is connected to the main beam 9 by bolts. The vertical height of the end of the bracket 16 close to the first flat beam 7 from the first flat beam 7 is defined as H, and the vertical height of the top of the slider from the first flat beam 7 is h, H>h, where H and h are positive numbers greater than 0.

[0090] In some other embodiments, a back plate is welded to the back of the blade of the riving knife 13, and a Y-shaped frame is welded to the side of the back plate facing the tail plate 10. The top of the Y-shaped frame is a U-shaped groove, and a screw facing the tail plate 10 is fixed to the center of the groove. Threaded holes are provided on the left and right groove walls of the U-shaped groove. The piston end of the hydraulic cylinder 12 is threadedly connected to the screws, and other screws can be used to connect the left groove wall of the U-shaped groove, the piston end, and the right groove wall of the U-shaped groove in sequence to fix the piston end, thereby limiting the stroke of the piston end and protecting the hydraulic cylinder 12.

[0091] By presetting the H and h parameters, the clearances and relative heights between the components are ensured to meet design requirements, allowing the slider to slide and cut the wood at the desired position, achieving both force balance and motion accuracy. By designing the H and h data to create a gap between the bracket 16 and the working beam, not only does this allow the slider to slide smoothly, but also allows some wood debris to fall through the gap after the wood is chopped by the chopper 13, preventing obstruction and improving chopping efficiency.

[0092] The engine 5 drives the gear pump 6, which circulates the hydraulic oil in the fuel tank 2 within a sealed oil circuit. The reversing valve 14 then controls the movement of the hydraulic cylinder 12. The entire energy conversion process relies on the interplay of mechanical transmission, hydraulic drive, and sealing technology to ensure efficient conversion of power from the engine 5 into hydraulic energy, which in turn is converted into linear motion of the splitter 13. During operation, the engine 5 provides continuous power, the gear pump 6 hydraulicizes this power, and the reversing valve 14 adjusts the flow of hydraulic oil according to control requirements. The hydraulic cylinder 12 utilizes oil pressure to drive the piston movement, which is fixedly connected to the splitter 13, directly driving the wood splitting process.

[0093] In some other embodiments, the foot support 4 is a swivel foot support 4 , and the rotation angle range of the swivel foot support 4 is [0°, 105°].

[0094] The rotating leg support 4 is conventional technology and includes a main support frame and a tension spring. The main support frame is connected to the machine frame 1 via screws, with a locking frame limiting counterclockwise rotation at the connection point. During towing, the main support frame is retracted and secured; during operation, it rotates to the desired angle to support the wood splitter. The tension spring is connected between the machine frame 1 and the main support frame via a fixing pin. The locking frame is secured to the main support frame via screws, with the ends bent 140°. Spring latches are welded to both sides of the main support frame and mate with the spring latches on the machine frame 1. The ends of the tension spring are designed with arc-shaped hooks, with the inner diameter of the hooks matching the outer diameter of the spring latches, ensuring that the tension spring will not fall out after installation. A fixing latch with a curved end is also welded to the side of the main support frame. A rubber stopper can also be installed on the machine frame 1 to secure the latch in place during towing, preventing the main support frame from falling. The rotating leg support 4 allows the frame 1 to adjust its angle during installation or operation to suit different work environments, ensuring balanced force distribution during the chopping process. The rotation design can provide multi-angle support, disperse the load, reduce single-point stress, and avoid equipment overturning or local fatigue. By setting a limited rotation range, the geometric shape and stress state of the support can be controlled, and the principle of statics can be used to place the overall center of gravity in a more reasonable position, thereby enhancing the stability of the equipment. In some embodiments, such as Figures 1 and 2 As shown, a safety chain 17 and a handle 18 are provided for pulling and grasping.

[0095] In some embodiments, a female flange is installed on the outer wall of the oil tank 2, the female flange is connected to a male flange, and an interface connecting the inside and outside of the oil tank 2 is installed on the male flange. The end of the hose for connecting the reversing valve 14 and the oil tank 2 is air-tightly connected to the interface, and one end of the interface located inside the oil tank 2 is threadedly connected to an oil return filter.

[0096] The connection between the male and female flanges secures high-precision seals, preventing hydraulic oil leakage and ensuring the sealing performance of oil line connections meets design requirements, guaranteeing stable operation of the hydraulic system. The addition of a return oil filter filters impurities, keeping the hydraulic oil clean; it also evenly disperses the hydraulic oil, optimizing system performance and reducing fluid shock and pressure fluctuations.

[0097] In some embodiments, a reinforcing rib 19 is welded to the main beam 9. The top of the reinforcing rib 19 is welded to the bottom surface of the first flat beam 7, and the bottom of the reinforcing rib 19 is welded to the top surface of the second flat beam 8. The base of the bracket 16 is bolted to the reinforcing rib 19. The distribution of the reinforcing rib 19 evenly transfers the stress generated within the working beam, avoiding local stress concentration.

[0098] In some embodiments, bracket 16 is defined as a receiving surface for receiving the wood, and a hole is provided on the receiving surface. When bracket 16 bears the weight of the wood, the hole structure can reduce the weight of bracket 16 and also provide ventilation and debris removal. The hole design reduces local weight and improves force distribution, alleviating to some extent the local stress concentration caused by wood loading.

[0099] In some embodiments, the surface of the baffle 11 that receives the wood is defined as a blocking surface, and a wedge-shaped block protrudes outward from the blocking surface. The wedge-shaped block faces the wood and can stabilize the wood when placed, and can also assist in splitting the wood, thereby improving the accuracy of wood positioning and the efficiency of wood splitting.

[0100] In some embodiments, the slider includes a first plate 20, a second plate 21 and a third plate 22, the riving knife 13 is fixed to the top surface of the first plate 20, the first plate 20 is parallel to the third plate 22, there are two second plates 21 and both are sandwiched between the first plate 20 and the third plate 22, the thickness of the second plates 21 is greater than the thickness of the first flat beam 7, the first flat beam 7 is sandwiched between the two second plates 21, the top surface of the second plate 21 is flush with the top surface of the first flat beam 7, and the distance between the two second plates 21 is greater than the width of the first flat beam 7.

[0101] The slider structure is designed so that two second plates 21 can be positioned at either end of the gap between the first plate 20 and the third plate 22. Bolts pass through the first, second, and third plates 20, 21, 22 to securely mount the blade 13. The multi-plate assembly optimizes the stress state and stability of the motion trajectory. This multi-plate assembly utilizes the principle of load distribution to evenly distribute external forces across each layer. Setting the plate spacing and thickness ensures smooth slider movement.

[0102] In some embodiments, the surfaces of the first plate 20, the second plate 21, and the third plate 22 facing the first flat beam 7 are covered with a lubricating layer. The lubricating layer is designed to reduce frictional resistance between the slider and the first flat beam 7, slowing wear and ensuring smooth sliding and accurate positioning of the riving knife 13.

[0103] The working principle of this design is as follows: In the initial state, hydraulic oil is stored in the fuel tank 2, and the gear pump 6 is in standby mode. The reversing valve 14 is in the neutral or locked position. When wood is placed on the bracket 16 and needs to be chopped, the engine 5 is started, which drives the gear pump 6. The gear pump 6 begins to draw oil from the fuel tank 2 and delivers the pressurized oil to the reversing valve 14 through the oil inlet. When the operator operates the reversing valve 14, the valve core moves by operating the single handle of the reversing valve 14, changing the oil flow path. For example, the high-pressure oil is distributed to the chamber of the hydraulic cylinder 12. As the oil pressure in the chamber increases, the piston is pushed to move. The operator changes the position of the reversing valve 14 again, returning the oil to the reversing valve 14, causing the piston to move in the opposite direction. The entire process repeats until the wood is chopped.

[0104] By using a wood splitter provided by the present invention, the speed of the wood splitting action can be increased by changing the force-bearing area of ​​the hydraulic cylinder 12 and increasing the flow rate while keeping the power of the engine 5 unchanged. The time of each wood splitting can be reduced from the conventional 12 to 15 seconds to 6 to 8 seconds, thereby increasing the number of cycles and reducing the single cycle time T. The single cycle time T=t 伸出 +t 退回 ; Use the following formula to calculate the single cycle time of the wood splitter when processing 25 tons of wood:

[0105] t=V / Q;

[0106] V=A C ×L S ;

[0107] Wherein, V refers to the volume of liquid, and the liquid of the present invention is hydraulic oil;

[0108] Q refers to the flow rate of hydraulic oil;

[0109] A C Refers to the cross-sectional area of ​​the hydraulic cylinder piston;

[0110] L S Refers to the stroke of the hydraulic cylinder;

[0111] In the wood splitter provided by the present invention, the stroke length of the hydraulic cylinder 12 is L S , in m, the diameter of the piston rod of the hydraulic cylinder 12 is d, in m; the flow rate of the hydraulic oil is Q, in m 3 / min; the cylinder diameter of the hydraulic cylinder 12 is D, in meters. The cycle time T is calculated by the following steps:

[0112] 1. Calculate the extended working area A 伸出 =π×D 2 / 4;

[0113] 2. Calculate A 退回 =π×(D 2 -d 2 ) / 4;

[0114] 3. Calculate V 伸出 =A 伸出 ×L S ; V 退回 =A 退回 ×L S ;

[0115] 4 Calculate t 伸出 =V 伸出 / Q;t 退回 =V 退回 / Q;

[0116] 5Calculate the cycle time T = t 伸出 +t 退回 .

[0117] In the prior art, a conventional wood splitter takes 12 to 15 seconds to process 25 tons of wood in a single cycle. However, the wood splitter provided by the present invention can process 25 tons of wood in a single cycle in a time interval of 12 to 15 seconds. S , d, Q, and D values ​​show that the time spent on a single cycle when processing 25 tons of wood is 6 to 8 seconds, which is shorter and more efficient than the existing technology.

[0118] When using the wood splitter provided by the present invention to process wood in a single cycle, it is necessary to limit the factors that affect the wood splitter's processing time. The most important of these is to limit the diameter of the interface of the oil inlet of the reversing valve 14 for connecting the hose to the gear pump. The following calculation process is designed to obtain the diameter of the interface of the oil inlet of the reversing valve 14 for connecting the hose to the gear pump 6 so that the hydraulic cylinder 12 completes a single cycle in the shortest time:

[0119] 1. Theoretical lossless speed calculation:

[0120] Without considering pipeline losses, the theoretical extension speed of the piston v0 is:

[0121]

[0122] Among them, Q p Refers to the rated flow of gear pump 6;

[0123] The corresponding one-way time t0 is:

[0124]

[0125] 2. Calculation of hose loss along the way

[0126] Pressure loss of fluid along the hose Δp lossUsing the Darcy–Weisbach formula:

[0127]

[0128] Among them, L h Refers to the length of the hose connecting the oil inlet of the reversing valve 14 and the gear pump 6;

[0129] D1 refers to the inner diameter of the hose connecting the oil inlet of the reversing valve 14 and the gear pump 6;

[0130] ρ refers to the density of hydraulic oil;

[0131] v h Refers to the volume of the hose connecting the oil inlet of the reversing valve 14 and the gear pump 6;

[0132] A h Refers to the cross-sectional area of ​​the hose connecting the oil inlet of the reversing valve 14 and the gear pump 6;

[0133] λ refers to the friction coefficient corresponding to the Reynolds number of the hose, and its value is 0.025;

[0134] Will Substituting, we can write

[0135]

[0136] This formula shows that the smaller the pipe diameter D, the more rapidly the loss increases (∝D -5 ).

[0137] 3. Calculate lossy speed and one-way time

[0138] The effective pressure P that can actually be used for the piston eff Approximately

[0139] P eff =P max -Δp loss ,

[0140] Among them, P max Refers to the maximum pressure of the hydraulic cylinder;

[0141] The corresponding flow attenuation Q eff Can be roughly regarded as

[0142]

[0143] So the actual piston speed v1

[0144]

[0145] Corresponding one-way time t move (D)

[0146]

[0147] 4. Hose filling time

[0148] At the beginning of each cycle, fresh oil in the hose is pumped into the hose. The pumping time is t fill (D)

[0149]

[0150] This means that the larger the pipe diameter, the larger the volume and the longer the filling time.

[0151] 5. Total cycle time model

[0152] Considering the extension and return as two identical single strokes, the effect of the return oil port size on the return speed can be ignored for simplicity. The total time T(D) for a single cycle is:

[0153] T(D)≈2[t fill (D)+t move (D)],

[0154] Substituting into the above formula, we can get

[0155]

[0156] in is a constant.

[0157] 6. Find the optimal pipe diameter D opt

[0158] make

[0159]

[0160] Taking the derivative of the total time T(D) of a single cycle with respect to D1, we can get the optimal pipe diameter D. opt The implicit equation of .

[0161] The following is an example: For example, with the following typical parameters

[0162] Q p =1.33×10 -4 m 3 / s

[0163] P max =2.0×10 7 Pa

[0164] ρ=850kg / m 3

[0165] λ=0.025;L h =2m

[0166] Ac =0.00636m 2 ;L s =0.40m

[0167] Solve

[0168] D opt ≈0.01905m≈19.05mm,

[0169] That's about 3 / 4 inch.

[0170] Therefore: When D < 19.05 mm: the pipeline pressure loss increases sharply, the flow rate decays seriously, the movement speed decreases, and t move , the cycle time increases.

[0171] When D>19.05mm: Although the loss is small, the pipe volume increases and the filling time t fill Growth leads to an increase in total time.

[0172] When D≈19mm, the compromise between the two is optimal, ultimately resulting in the shortest single cycle time and the highest efficiency.

[0173] Therefore, by limiting the diameter of the pipe from the oil inlet of the reversing valve 14 to the interface of the gear pump 6, the best wood splitting cycle efficiency can be achieved.

[0174] In summary, the wood splitter provided by the present invention reduces the time for each wood splitting operation from the conventional 12 to 15 seconds to 6 to 8 seconds. Each time the wood splitting operation is performed, the airflow generated by the high-speed movement of the splitter itself is used to efficiently blow away the wood chips and residues on the surface of the working beam, thereby reducing the damage caused by these residues to the surface of the splitter. Since the power of the splitter involved in the present invention varies greatly during operation, a fixing method using tires and foot supports is adopted to fully utilize the characteristics of the tires to alleviate the kinetic energy impact during operation. Similarly, the strength of the working beam of the present invention is also stronger and more reliable than that of the prior art. These structures ensure that high-speed wood splitting is feasible.

[0175] The technical solution described in this invention achieves a 92% reduction in the rate of debris and debris blown off the wood splitter blade's path. This rate, of course, is nearly 100% for debris with a radius greater than 0.5 mm that could interfere with blade movement. Furthermore, because the splitting operation time is shortened, even though engine power consumption increases, the energy consumption per unit of wood splitting is actually reduced.

[0176] By calculating the diameter of the reversing valve's oil inlet for the hose connecting to the gear pump, the efficiency of the splitting cycle is significantly improved. By scientifically calculating the diameters of the reversing valve's oil inlet and the gear pump's connection, the optimal diameter is selected, achieving an optimal balance between hydraulic oil flow resistance in the system and pipe filling speed. This minimizes the filling and movement time of the hydraulic cylinder, minimizing the time required for each complete splitting cycle of the wood splitter and improving overall operating efficiency. Energy consumption is reduced and the burden on the hydraulic system is alleviated. If the diameter is too small, flow resistance increases and pressure loss increases, forcing the gear pump and engine to operate under high load for extended periods, resulting in increased energy consumption and heat generation. If the diameter is too large, the fluid flow rate decreases, slowing system response and causing unnecessary energy loss. By optimizing the diameter, the system operates at the appropriate flow rate and pressure, significantly reducing energy consumption and extending system life. Ensure the stability and reliability of the hydraulic system: When the calibers are properly matched, hydraulic shock is reduced, pipeline vibration is reduced, and the hydraulic oil temperature rises slowly, which helps maintain oil viscosity and lubrication properties, thereby extending the life of core components such as hydraulic cylinders, reversing valves, and gear pumps, and improving the overall reliability and safety of the wood splitter. Reduce repair frequency and maintenance costs: Due to the small fluid shock, light component wear, and reduced equipment failure rate, the number of subsequent maintenance and the frequency of parts replacement are also greatly reduced, thus saving a lot of maintenance costs. The wood splitter's movements during the splitting process are smooth and coherent, with sufficient power, and no jamming or delays. The operator has a good user experience, and production efficiency and work comfort have been significantly improved.

[0177] While the present invention has been disclosed above with reference to preferred embodiments, this is not intended to limit the present invention. Persons skilled in the art will readily appreciate that various modifications and variations can be made without departing from the spirit and scope of the present invention. Therefore, the scope of protection of the present invention shall be determined by the claims.

Claims

1. A wood splitter, comprising a frame, one end of the frame being connected to a fuel tank, tires being mounted on both sides of the fuel tank, and the other end of the frame being connected to a foot support, characterized in that: An engine and a gear pump are installed outside the oil tank, the output shaft of the engine is drivingly connected to the drive shaft of the gear pump, and the oil suction port of the gear pump is connected to the oil tank; The frame is provided with a working beam, comprising a first flat beam, a second flat beam, and a main beam. The first flat beam and the second flat beam are parallel to each other, the main beam is welded between the first flat beam and the second flat beam, and the second flat beam is connected to the frame by bolts. A tail plate that is upwardly tilted from the first flat beam is welded to one end of the working beam close to the foot support, and a baffle that is higher than the top surface of the first flat beam is welded to the other end of the working beam. The bottom of the hydraulic cylinder is connected to the tail plate via bolts, and the piston end of the hydraulic cylinder is detachably connected to the blade back of the cleaver; the blade back of the cleaver is provided with side air deflectors extending to the edges of both sides of the cleaver; the chamber of the hydraulic cylinder is connected to the output interface of the reversing valve via a hose, the oil inlet of the reversing valve is connected to the gear pump via a hose, and the oil return port of the reversing valve is connected to the oil tank via a hose; A slider is slidably connected to the first flat beam, and the blade of the cleaver is fixed on the slider; A bracket is installed between the hydraulic cylinder and the baffle, and the bracket is used to receive the wood when the wood is being chopped.

2. A wood splitter according to claim 1, characterized in that: The side wing air guide plates are arranged on both sides of the riving knife to form a guide curved surface. The guide curved surface is 5 to 6 cm close to the blade of the riving knife. The guide curved surface and the surface of the riving knife facing away from the blade have a backward tilt angle of 15° to 25°. The curvature of the guide curved surface at the end away from the working beam is greater than the curvature of the guide curved surface at the end close to the working beam. The guide curved surface has a radial involute-like distribution from the end away from the working beam to the end close to the working beam (to avoid dynamic imbalance).

3. A wood splitter according to claim 1 or 2, characterized in that: A stopper is detachably connected to the first flat beam, and a slider is slidably connected to the first flat beam, and the bottom of the riving knife is fixed on the slider; the stopper is provided with an opening recessed in the upper surface of the first flat beam on the side facing the baffle, and when the slider slides between the opening and the baffle, the stopper is used to limit the distance the slider slides toward the tail plate.

4. A wood splitter according to claim 1 or 2, characterized in that: There are two brackets, which are located on both sides of the first flat beam respectively. The base of each bracket is connected to the main beam by bolts. The vertical height of the end of the bracket close to the first flat beam from the first flat beam is defined as H, and the vertical height of the top of the slider from the first flat beam is defined as h, H>h, where H and h are positive numbers greater than 0.

5. A wood splitter according to claim 1 or 2, characterized in that: The bracket is defined as a receiving surface for receiving wood, and an opening penetrating the receiving surface is provided on the receiving surface.

6. A wood splitter according to claim 1 or 2, characterized in that: A female flange is installed on the outer wall of the oil tank, and the female flange is connected to a male flange. An interface connecting the inside and outside of the oil tank is installed on the male flange. The end of the hose connecting the reversing valve and the oil tank is air-tightly connected to the interface, and one end of the interface located inside the oil tank is threadedly connected to an oil return filter.

7. A wood splitter according to claim 1, characterized in that: Reinforcement ribs are welded on the main beam, the top of the reinforcement ribs is welded to the bottom surface of the first flat beam, the bottom of the reinforcement ribs is welded to the top surface of the second flat beam, and the base of the bracket is connected to the reinforcement ribs by bolts.

8. A wood splitter according to claim 1, characterized in that: The surface of the baffle used for receiving the wood is defined as a blocking surface, and a wedge-shaped block is protruded outwardly from the blocking surface.

9. A wood splitter according to claim 1, characterized in that: The slider includes a first plate, a second plate and a third plate. The chopping knife is fixed on the top surface of the first plate. The first plate is parallel to the third plate. There are two second plates and both are sandwiched between the first plate and the third plate. The thickness of the second plates is greater than the thickness of the first flat beam. The first flat beam is sandwiched between the two second plates. The top surface of the second plate is flush with the top surface of the first flat beam. The distance between the two second plates is greater than the width of the first flat beam.

10. A wood splitter according to claim 1, characterized in that: When the oil inlet of the reversing valve is connected to the gear pump through a hose, the diameter of the interface of the gear pump is the calculated diameter, and the calculation method includes: Step 1: Calculate the theoretical lossless speed; Without considering pipeline losses, the theoretical extension speed v0 of the piston is: Among them, Q p Refers to the rated flow of the gear pump; A c Refers to the cross-sectional area of ​​the hydraulic cylinder piston; The corresponding one-way time t0 is: Among them, L s Refers to the rated flow of the gear pump; Step 2: Calculate the loss along the hose; Calculate the pressure loss Δp of the fluid along the hose using the Darcy-Weisbach formula loss : Among them, L h Refers to the length of the hose connecting the oil inlet of the reversing valve and the gear pump; D1 refers to the inner diameter of the hose connecting the oil inlet of the reversing valve and the gear pump; ρ refers to the density of hydraulic oil; v h Refers to the volume of the hose connecting the oil inlet of the reversing valve and the gear pump; A h Refers to the cross-sectional area of ​​the hose connecting the oil inlet of the reversing valve and the gear pump; λ refers to the friction coefficient corresponding to the Reynolds number of the hose, and its value is 0.025; Will Substituting, This formula shows that the smaller the pipe diameter D is, the more rapidly the loss increases; Step 3: Calculate the lossy speed and one-way time; The effective pressure P that can actually be used for the piston eff P eff =P max -Δp loss , Among them, P max Refers to the maximum pressure of the hydraulic cylinder; The corresponding flow attenuation Q eff Can be roughly regarded as So the actual piston speed v1 Corresponding one-way time t move (D) Step 4: Calculate the hose filling time; At the beginning of each cycle, fresh oil in the hose is pumped into the hose, and the pumping time is t fill (D) This means that the larger the pipe diameter D, the larger the volume and the longer the filling time; Step 5: Calculate the total cycle time model; Considering the extension and return as two identical single strokes, the influence of the return oil port size on the return speed can be ignored for simplicity. The total time of a single cycle T(D) is T(D)≈2[t fill (D)+t move (D)], Substituting into the above formula, we can get in is a constant; Step 6: Calculate the optimal pipe diameter d opt ; For the total time of a single cycle T(D), let Obtain the optimal pipe diameter.

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