A hydraulic fluid inertia device and system with variable stroke force and an inertia coefficient adjustment method

Abstract

The present invention relates to a hydraulic fluid inertia device with variable stroke force, a system, and an inertia coefficient adjustment method, comprising a first piston rod, a first hydraulic cylinder, a first helical tube, a first piston connector, a second piston connector, a second piston rod, a second piston, a second hydraulic cylinder, a second helical tube, and a transition chamber; the first and second helical tubes are respectively located outside the cylinder bodies of the first hydraulic cylinder and the second hydraulic cylinder, the transition chamber is located between the first hydraulic cylinder and the second hydraulic cylinder, the second piston is located inside the cylinder body of the second hydraulic cylinder, the second piston rod is fixedly connected to the second piston, and passes through the second hydraulic cylinder; the piston connector is fixed to the piston rod, the first piston connector and the second piston connector are located in the transition chamber, the first piston rod and the second piston rod are coaxial, and the end faces of the first piston connector and the second piston connector are axially aligned. Compared with the prior art, the present invention realizes a hydraulic fluid inertia device with variable stroke force, and the inertia coefficient is easy to adjust, and has the advantages of simple structure and easy implementation.

Description

Technical Field

[0001] The present invention relates to the field of high-end equipment manufacturing, and in particular to a hydraulic fluid inertia device with variable stroke force and an inertia coefficient adjustment method. Background Art

[0002] A variety of fluid inertia devices have been developed, including a piston-rod-embedded fluid inertia container, a double-tube fluid inertia container, and a passive frequency-adaptive fluid inertia container. Most of these fluid inertia containers are merely innovative in their operating form, failing to achieve variable inertia coefficients and therefore have limited applicability. One passive frequency-adaptive fluid inertia container only achieves frequency-based adaptive changes, failing to achieve variable inertia coefficients based on travel. However, in practical applications, such as inter-layer installation within a frame structure, inertia containers with variable inertia coefficients based on travel often have greater potential.

[0003] Utility model CN214465778U discloses a viscous fluid inertia damper, comprising a connecting tube housing a piston and a second chamber housing the deeper portion of the piston rod. A regulating valve assembly switches the connection between the first and second regulating tubes between parallel and series, thereby adjusting the inertia coefficient. The regulating valve's structure for changing the inertia coefficient is complex and cannot adjust the inertia coefficient with stroke. Summary of the Invention

[0004] The purpose of the present invention is to overcome the defects of the above-mentioned prior art and provide a hydraulic fluid inertia device, system and inertia coefficient adjustment method with variable stroke force.

[0005] The purpose of the present invention can be achieved by the following technical solutions:

[0006] According to one aspect of the present invention, a hydraulic fluid inertia device with variable stroke force is provided, comprising a first piston rod, a first hydraulic cylinder, a first helical tube, a first piston connector, a second piston connector, a second piston rod, a second piston, a second hydraulic cylinder, a second helical tube and a transition chamber; the first helical tube is distributed outside the cylinder body of the first hydraulic cylinder, the second helical tube is distributed outside the cylinder body of the second hydraulic cylinder, the transition chamber is located between the first hydraulic cylinder and the second hydraulic cylinder, the second piston is located in the cylinder body of the second hydraulic cylinder, the second piston rod is fixedly connected to the second piston and passes through the second hydraulic cylinder; the first piston connector is fixed to the first piston rod, the second piston connector is fixed to the second piston rod, the first piston connector and the second piston connector are located in the transition chamber, the first piston rod and the second piston rod are coaxial, and the end faces of the first piston connector and the second piston connector are axially aligned.

[0007] Furthermore, it also includes a first piston, the first piston is located in the cylinder body of the first hydraulic cylinder, and the first piston rod is fixedly connected to the first piston.

[0008] Furthermore, the first piston connector and the second piston connector are both flat structures, the surface of the first piston connector facing the second piston connector is a plane, and the surface of the second piston connector facing the first piston connector is also a plane.

[0009] Furthermore, the cross section of the first piston matches the cross section shape and size of the first hydraulic cylinder, and the cross section of the second piston matches the cross section shape and size of the second hydraulic cylinder.

[0010] Furthermore, the action stroke of the first piston in the first hydraulic cylinder is greater than the action stroke of the second piston in the second hydraulic cylinder.

[0011] Furthermore, it also includes permanent magnets, which include left-side permanent magnets and right-side permanent magnets. The left-side permanent magnet is installed on the right side of the second piston, and the left-side permanent magnet is installed on the right side of the second hydraulic cylinder. The left-side permanent magnet and the right-side permanent magnet stimulate mutual repulsion.

[0012] Furthermore, a first oil port and a second oil port are opened in the first hydraulic cylinder, and the first oil port and the second oil port are located on opposite sides of the first piston, and the first oil port and the second oil port are connected by a first spiral tube arranged outside the first hydraulic cylinder; a third oil port and a fourth oil port are opened in the second hydraulic cylinder, and the third oil port and the fourth oil port are located on opposite sides of the second piston, and the third oil port and the fourth oil port are connected by a second spiral tube arranged outside the first hydraulic cylinder.

[0013] Furthermore, it also includes a connecting piece, which is connected to the structure that needs shock absorption.

[0014] Furthermore, the hydraulic system includes a hydraulic fluid inertia device with variable stroke force.

[0015] According to another aspect of the present invention, a method for adjusting the inertia coefficient is provided, comprising the following steps:

[0016] Obtain the required inertia coefficient for the application scenario, adjust the piston rod's travel, and calculate the inertia coefficient of the hydraulic fluid inertia device with variable stroke force until the required inertia coefficient is met;

[0017] The calculation expression of the inertia coefficient of the hydraulic fluid inertia device with variable stroke force is:

[0018]

[0019] Where m inis the inertia coefficient, x is the movement stroke of the piston rod, x1 is the movement stroke of the piston rod when the first piston rod connecting part contacts the second piston rod connecting part, x2 is the maximum stroke of the first piston rod, A1 is the working area of ​​the first piston and the second piston, A2 is the cross-sectional area of ​​the spiral tube and the spiral tube, r1 is the radius, h is the pitch, l1 is the length of the first spiral tube, l2 is the length of the second spiral tube, and ρ is the density of the liquid in the hydraulic cylinder.

[0020] Compared with the prior art, the present invention has the following advantages:

[0021] 1. The present invention provides two sets of pistons, piston rods and hydraulic cylinder assemblies aligned left and right. The first piston rod performs axial reciprocating motion under external drive, driving the first piston to slide inside the first hydraulic cylinder, pushing the fluid inside the first hydraulic cylinder to move, causing the fluid to move in the external pipe of the first hydraulic cylinder, thereby simulating the mechanical behavior of the inertia volume; when the first piston rod moves to a certain position, the second piston rod in contact with the other end of the first piston will drive the second piston to slide inside the second hydraulic cylinder. At this time, the first hydraulic cylinder and the second hydraulic cylinder work simultaneously, and the inertia volume coefficient is the sum of the two, thereby realizing a hydraulic fluid inertia volume device with variable stroke force; when the first piston rod moves in the reverse direction, it will only drive the first piston to move, and the second piston will be reset under the action of the permanent magnet at the bottom of the second hydraulic cylinder; the present invention realizes a hydraulic fluid inertia volume device with variable stroke force, which can adapt to various shock absorption occasions;

[0022] 2. The present invention conducts a theoretical analysis on the structural characteristics of the hydraulic fluid inertia device with variable stroke force, and obtains a calculation formula for the inertia coefficient under different strokes. The movement stroke of the piston rod can be quickly adjusted according to the inertia coefficient requirements of the application scenario.

[0023] 3. The present invention can easily adjust the inertia coefficient of each level by replacing the sizes of the two hydraulic cylinders, which is highly flexible in practical applications;

[0024] 4. The mechanical form of the present invention is simple, easy to implement, and can adapt to the installation requirements of small or special spaces. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 Schematic diagram of the structure of the hydraulic fluid inertia device with variable stroke force

[0026] In the figure, 1, connecting part, 2, first piston rod, 3, first piston, 4, first oil port, 5, first hydraulic cylinder, 6, first spiral tube, 7, second oil port, 8, first piston rod connecting part, 9, second piston rod connecting part, 10, second piston rod, 11, second piston, 12, third oil port, 13, second hydraulic cylinder, 14, second spiral tube, 15, fourth oil port, 16, permanent magnet. DETAILED DESCRIPTION

[0027] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are part of the embodiments of the present invention, not all of them. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts should fall within the scope of protection of the present invention.

[0028] like Figure 1 As shown, the present invention relates to a hydraulic fluid inertia device with variable stroke force, comprising a connecting member 1, a first piston rod 2, a first piston 3, an oil port 4, a first hydraulic cylinder 5, a first spiral tube 6, an oil port 7, a first piston rod connecting member 8, a second piston rod connecting member 9, a second piston rod 10, a second piston 11, an oil port 12, a second hydraulic cylinder 13, a second spiral tube 14, an oil port 15, and a permanent magnet 16. The connecting member 1 is connected to a structure requiring shock absorption, the first piston rod 2 is fixed to the first piston 3, the first piston 3 is installed in the first hydraulic cylinder 5, and divides the liquid in the first hydraulic cylinder 5 into two parts, an oil port 4 and an oil port 7 are provided in the first hydraulic cylinder 5, the oil port 4 and the oil port 7 are located on opposite sides of the first piston 3, and the oil port 4 and the oil port 7 are connected by a first spiral tube 6 arranged outside the first hydraulic cylinder 5, the axial movement of the first piston rod 2 under the action of an external driving force causes the first piston rod connecting member 8 to contact the second piston rod connecting member 9, and push The second piston rod 10 is driven to move axially. The second piston rod 10 is fixedly connected to the second piston 11. The second piston 11 is installed in the second hydraulic cylinder 13 and divides the liquid in the second hydraulic cylinder 13 into two parts. The second hydraulic cylinder 13 has an oil port 12 and an oil port 15. The oil port 12 and the oil port 15 are located on opposite sides of the second piston 13. The oil port 12 and the oil port 15 are connected by a second spiral tube 14 arranged outside the first hydraulic cylinder 13. The permanent magnet 16 is respectively fixed to the right side of the second piston 11 and the bottom of the second hydraulic cylinder 13.

[0029] The first piston rod 2 moves axially under external drive, driving the first piston 3 to slide inside the first hydraulic cylinder 5, so that the liquid in the first hydraulic cylinder 5 enters and exits the first spiral tube 6 through the oil port 4 and the oil port 7, thereby simulating the mechanical behavior of the inertia volume. When the first piston rod 2 moves to a certain stroke, it will drive the first piston rod connecting member 8 to contact the second piston rod connecting member 9 and push the second piston rod 10 to move axially. The second piston rod 10 drives the second piston 11 to slide inside the second hydraulic cylinder 13, so that the liquid in the second hydraulic cylinder 13 enters and exits the second spiral tube 14 through the oil port 12 and the oil port 15, simulating the mechanical behavior of the inertia volume, thereby providing an additional inertia coefficient. When the first piston rod 2 moves in the opposite direction, the second piston 11 will be reset under the action of the permanent magnet 16.

[0030] The inertia coefficient of the hydraulic fluid inertia device with variable stroke force proposed in the present invention is derived as follows:

[0031] like Figure 1 As shown, assuming that the working area of ​​the first piston 3 and the second piston 11 is A1, the cross-sectional area of ​​the first helical tube 6 and the second helical tube 14 is A2, the radius is r1, the pitch is h, the length of the first helical tube 6 is l1, the length of the second helical tube 14 is l2, the density of the liquid in the first hydraulic cylinder and the second hydraulic cylinder is ρ, when the first piston rod 2 moves to the right to x1, the first piston rod connecting member 8 contacts the second piston rod connecting member 9, and the maximum stroke of the first piston rod 2 is x2.

[0032] During the analysis, it is assumed that the piston is completely sealed, the liquid in the hydraulic cylinder flows completely into the spiral tube, and the fluid is incompressible.

[0033] When the rightward movement of the first piston rod 2 is 0 to x1:

[0034] The dynamic model of the fluid in the first hydraulic cylinder passing through the spiral tube can be expressed as:

[0035]

[0036] Where: F1 is the force applied to the first screw, m in1 is the inertia coefficient, and x is the relative displacement of the first piston relative to the first hydraulic cylinder.

[0037] The mass m1 of the fluid in the spiral tube 6 can be expressed as:

[0038] m1=ρA2l1 (2)

[0039] When the stroke of the first piston rod 2 is x, according to the principle of conservation of fluid volume, we can obtain:

[0040]

[0041] Where: h is the pitch of the spiral tube, r1 is the spiral radius of the slender spiral tube, and θ is the corresponding turning angle when the fluid enters the spiral tube.

[0042] The moment of inertia J generated by the fluid rotating in the spiral tube is:

[0043] J=m1r1 4 (4)

[0044] According to the law of conservation of energy, we can get:

[0045]

[0046] Substituting equations (2), (3), and (4) into equation (5), we can obtain the inertia coefficient m: in1 for:

[0047]

[0048] When the rightward movement of the first piston rod 2 is x1 to x2:

[0049] At this time, the second piston cylinder starts to work, and the inertia coefficient generated can be obtained according to the above derivation:

[0050]

[0051] In summary, the inertia coefficient m of the device is in The formula is:

[0052]

[0053] Where x is the stroke of the first piston rod moving to the right.

[0054] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any person skilled in the art can easily conceive of various equivalent modifications or substitutions within the technical scope disclosed in the present invention, and such modifications or substitutions are intended to be within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be subject to the scope of protection of the claims.

Claims

1. A hydraulic fluid inertia device with variable stroke force, characterized in that: The invention comprises a first piston rod (2), a first hydraulic cylinder (5), a first spiral tube (6), a first piston connector (8), a second piston connector (9), a second piston rod (10), a second piston (11), a second hydraulic cylinder (13), a second spiral tube (14) and a transition chamber; the first spiral tube (6) is distributed outside the cylinder body of the first hydraulic cylinder (5), the second spiral tube (14) is distributed outside the cylinder body of the second hydraulic cylinder (13), the transition chamber is located between the first hydraulic cylinder (5) and the second hydraulic cylinder (13), and the second piston (11) is located outside the cylinder body of the second hydraulic cylinder (13). Located in the cylinder body of the second hydraulic cylinder (13), the second piston rod (10) is fixedly connected to the second piston (11) and passes through the second hydraulic cylinder (13); the first piston connector (8) is fixed to the first piston rod (2), the second piston connector (9) is fixed to the second piston rod (10), the first piston connector (8) and the second piston connector (9) are located in the transition chamber, the first piston rod (2) and the second piston rod (10) are coaxial, and the end faces of the first piston connector (8) and the second piston connector (9) are axially aligned; It also includes a first piston (3), the first piston (3) is located in the cylinder body of the first hydraulic cylinder (5), and the first piston rod (2) is fixedly connected to the first piston (3); The action stroke of the first piston (3) in the first hydraulic cylinder (5) is greater than the action stroke of the second piston (11) in the second hydraulic cylinder (13); It also includes a permanent magnet (16), the permanent magnet (16) including a left permanent magnet and a right permanent magnet, the left permanent magnet is installed on the right side of the second piston (11), and the right permanent magnet is installed on the right side of the second hydraulic cylinder (13), and the magnetic poles of the left permanent magnet and the right permanent magnet repel each other; A first oil port (4) and a second oil port (7) are provided in the first hydraulic cylinder (5), the first oil port (4) and the second oil port (7) are located on opposite sides of the first piston (3), and the first oil port (4) and the second oil port (7) are connected via a first spiral tube (6) arranged outside the first hydraulic cylinder (5); a third oil port (12) and a fourth oil port (15) are provided in the second hydraulic cylinder (13), the third oil port (12) and the fourth oil port (15) are located on opposite sides of the second piston (11), and the third oil port (12) and the fourth oil port (15) are connected via a second spiral tube (14) arranged outside the second hydraulic cylinder (13).

2. A variable stroke force hydraulic fluid inertia device according to claim 1, characterized in that: The first piston connector (8) and the second piston connector (9) are both flat structures; the surface of the first piston connector (8) facing the second piston connector (9) is a plane, and the surface of the second piston connector (9) facing the first piston connector (8) is a plane.

3. The variable stroke force hydraulic fluid inertia device according to claim 1, characterized in that: The cross-section of the first piston (3) matches the cross-section shape and size of the first hydraulic cylinder (5), and the cross-section of the second piston (11) matches the cross-section shape and size of the second hydraulic cylinder (13).

4. The variable stroke force hydraulic fluid inertia device according to claim 1, characterized in that: It also includes a connecting member (1), which is connected to a structure requiring shock absorption.

5. A hydraulic system, characterized in that: The hydraulic system includes a hydraulic fluid inertia device with variable stroke force as described in any one of claims 1-4.

6. A method for adjusting the inertia coefficient of a hydraulic fluid inertia device with variable stroke force according to any one of claims 1 to 4, characterized in that: The following steps are involved: Obtaining the inertia coefficient requirement of the application scenario, adjusting the movement stroke of the piston rod, and calculating the inertia coefficient of the hydraulic fluid inertia device with variable stroke force until the inertia coefficient requirement is met; The calculation expression of the inertia coefficient of the hydraulic fluid inertia device with variable stroke force is: Where, is the coefficient of inertia, is the movement stroke of the first piston rod, is the movement stroke of the first piston rod when the first piston connector (8) contacts the second piston connector (9), is the maximum stroke of the first piston rod (2), is the working area of ​​the first piston (3) and the second piston (11), is the cross-sectional area of ​​the first helical tube (6) and the second helical tube (14), are the radii of the first helical tube (6) and the second helical tube (14), is the pitch of the first helical tube (6) and the second helical tube (14), is the length of the first spiral tube (6), is the length of the second helical tube (14), is the density of the liquid in the hydraulic cylinder.

Images