Hydraulic mem-inerter container device and applications thereof

Abstract

A hydraulic mem-inerter container device and applications thereof. The hydraulic mem-inerter container device comprises a first cylinder barrel, a first piston, and a spiral passage. The first cylinder barrel is divided by the first piston into a left cavity and a right cavity; and the spiral passage enables the left cavity and the right cavity of the first cylinder barrel to communicate, and the length of the spiral passage changes along with the change of the relative displacement of the first cylinder barrel and the first piston. The cylinder barrel and the piston serve as a first end point and a second end point that are independent and movable correspondingly. When used, the hydraulic mem-inerter container device can be connected to a system to control mechanical force. The hydraulic mem-inerter container device can serve as a regulation and control valve for an inerter and a damper.

Claims

1. A hydraulic mem-inerter device, comprising: a first cylinder; a first piston; and a helical path; wherein the first piston divides the first cylinder into left and right chambers, which are connected by the helical path; wherein a length of the helical path varies with the relative displacement between the first cylinder and the first piston; and wherein a momentum and relative velocity characteristic curve of the hydraulic mem-inerter device is a pinched hysteresis loop, and a momentum integral and relative displacement characteristic curve of it is a single-valued mapping.

2. The hydraulic mem-inerter device according to claim 1, wherein: the first cylinder has two internal surfaces with different diameters, namely the internal surface with major diameter and the internal surface with minor diameter, respectively; the outer surface of the first piston is matched with the internal surface with minor diameter of the first cylinder to divide the first cylinder into left and right chambers; and the outer surface of the first piston has a helical channel, such that, when inserted inside the first cylinder, a helical path formed between the helical channel and the internal surface with minor diameter can connect the left chamber with the right chamber of the first cylinder.

3. The hydraulic mem-inerter device according to claim 1, wherein: the first cylinder has two internal surfaces with different diameters, namely the internal surface with major diameter and the internal surface with minor diameter, respectively; the outer surface of the first piston is matched with the internal surface with minor diameter of the first cylinder to divide the first cylinder into left and right chambers; and the internal surface with minor diameter has a helical channel, such that, when the first piston is inserted inside the first cylinder, a helical path formed between the helical channel and the outer surface of the first piston can connect the left chamber with the right chamber of the first cylinder.

4. The hydraulic mem-inerter device according to claim 2, wherein the helical channel has a fixed helix pitch or a variable helix pitch.

5. Use of a hydraulic mem-inerter device according to claim 1 as a mem-dashpot, wherein: the first cylinder and the first piston of the hydraulic mem-inerter device are two independently movable terminals of mem-dashpot; the damping force and relative velocity characteristic curve of the mem-dashpot is a pinched hysteresis loop; and the momentum and relative displacement characteristic curve of it is a single-valued mapping.

6. Use of a hydraulic mem-inerter device according to claim 1 as a variable mass element, wherein any one of the first cylinder and the first piston of the hydraulic mem-inerter device is fixed.

7. Use of a hydraulic mem-inerter device according to claim 1 in a mechanical system to control or counteract the vibrational forces.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) Embodiments of the present invention will be further described with reference to the accompanying drawings.

(2) FIG. 1 is the schematic of a hydraulic inerter device.

(3) FIG. 2 is the triangular periodic table of elementary circuit elements.

(4) FIG. 3 is the triangular periodic table of elementary mechanical elements.

(5) FIG. 4 is the schematic of an external-helix hydraulic mem-inerter device.

(6) FIG. 5 is the schematic of an internal-helix hydraulic mem-inerter device.

(7) FIGS. 6a-6c are the inertance and mechanical characteristic curves of the mem-inerter device.

(8) FIGS. 7a-7d are the comparison of the characteristic curves between the mem-inerter and inerter device.

(9) FIGS. 8a-8c are the damping characteristic curves of the mem-inerter device.

(10) FIG. 9 is the schematic of a hydraulic mem-inerter device used as an adjustment and control valve.

(11) FIG. 10 is the schematic of a continuously adjustable inerter device.

(12) In the figures: 1—First cylinder; 2—Helical channel: 3—First piston; 4—First piston rod; 5—Internal surface with major diameter; 6—Internal surface with minor diameter; 7—Fluid; 8—First openings; 9—Hydraulic mem-inerter device; 10—Hydraulic tubes; 11—Hydraulic cylinder; 12—Second cylinder; 13—Second piston; 14—Second piston rod; 15—Second openings.

DETAILED DESCRIPTION

(13) Devices provided the present invention will be further described with reference to the accompanying drawings and embodiments.

(14) FIG. 4 illustrates a first embodiment of a hydraulic mem-inerter device, comprising a first cylinder 1, a first piston 3, and a fluid 7. The first cylinder 1 has two internal surfaces with different diameters, namely, the internal surface with major diameter 5 and the internal surface with minor diameter 6, respectively, and the interior of the first cylinder 1 is filled with a fluid 7. The outer surface of the first piston 3 is matched with the internal surface with minor diameter 6 of the first cylinder 1 to divide the first cylinder 1 into left and right chambers. The outer surface of the first piston 3 has a helical channel 2, such that, when inserted inside the first cylinder 1, a helical path formed between the helical channel 2 and the internal surface with minor diameter 6 can connect the left chamber with the right chamber of the first cylinder 1. Movement of the first piston 3 relative to the first cylinder 1 causes the fluid 7 to flow out from one chamber and into the other chamber via the helical path, which can generate an inertial force due to the moving mass of the fluid in the helical path. The first cylinder 1 may include one terminal, and the first piston 3 may include the other terminal of the device. Since the length of the helical path varies with the relative displacement between the terminals, the ratio of the inertial force to the relative acceleration, the inertance, varies with the relative displacement between them. Besides, the momentum and velocity characteristic curve of the mem-inerter device is a pinched hysteresis loop, and the momentum integral and displacement characteristic curve of it is a single-valued mapping.

(15) FIG. 5 illustrates a second embodiment of a hydraulic mem-inerter device. The difference of the two embodiments is that the helical channel 2 is located on the outer surface of the first piston 3 in the first embodiment, but on the internal surface with minor diameter 6 of the first cylinder 1 in the second embodiment.

(16) For the first and second embodiments, the helical channel 2 has a cross-section which is a semi-disc which is convenient for machining. Other cross-sectional shapes may also be employed as required. Similarly, the pitch of the helical channel 2 can be designed to a fixed value or a variable value. In addition, the first cylinder 1 can also be a valve body or a shell containing a chamber.

(17) The two devices of FIGS. 4 and 5 are implemented using the through-rod 4. Alternatives using a single rod with a floating piston or a double cylinders or other similar arrangements are equally feasible. Means to cause the fluid to flow are envisaged.

(18) In the embodiments shown in FIGS. 4 and 5, the characteristic parameter of the devices, namely the inertance, is not a constant. It can be varied with altering relative displacement. In other words, the inertance is a function of the relative displacement, and the function is determined by the diameter and width of the piston, the radius and pitch of the helical channel, the fluid density, etc.

(19) The following aspects illustrate that the device provided by the present invention is an implementation of an ideal mem-inerter element by FIG. 4.

(20) Consider the hydraulic inerter device shown in FIG. 1, which is a prior art. Let A.sub.1 be the effective cross-sectional area of the first piston 3, namely, the working area of the first piston 3. Let A.sub.2 be the cross-sectional area of the semicircular helical channel, be the channel length and p be the density of the fluid 7. Let F be the equal and opposite force applied to the terminals and x be the relative displacement between them. According to the International Patent PCT/GB2010/001491, the hydraulic mem-inerter depicted in FIG. 1 can be modelled as an ideal inerter element, as a result, the relative acceleration between the terminals and the force applied to them are related linearly as follows:
F=B{umlaut over (x)}  (1)
where B is the inertance in kg, it can be expressed as

(21) $\begin{array}{cc}B=\rho l\frac{A_1^2}{A_2}& \left(2\right)\end{array}$

(22) Let m.sub.F be the mass of the fluid in the channel, then Eq. (2) can be represented in the form

(23) $\begin{array}{cc}B={m_F\left(\frac{A_1}{A_2}\right)}^2& \left(3\right)\end{array}$

(24) It indicates that the inertance is directly proportional to the mass of the fluid in the channel, and to the square of the cross-sectional area ratio between the piston and the channel.

(25) Let D be the diameter of the piston, d be the diameter of the piston rod, r.sub.h be the radius of the helical channel, P be the pitch of the helix, and w be the piston width. Eq. (2) will be rewritten as follows:
B=b.sub.0w  (4)
where b.sub.0 is the inertance constant

(26) $b_0=\frac{\pi {\rho \left(D^2-d^2\right)}^2\sqrt{P^2+{\left(\pi D\right)}^2}}{8{\mathrm{Pr}}_h^2}$

(27) The mechanism can be designed to make the linear inerter into nonlinear or displacement-dependent. To this end, a modified cylinder with enlarged radius of the internal surface in the right half part is considered by the present invention as shown in FIG. 4, so that the length of a helical channel surrounded by the internal surface with minor diameter of the cylinder, namely, the length of the helical path, is changed during the motion of the piston, and the mass of the fluid in helical path is successively varied. According to Eq. (3) or Eq. (4), the inertance is consequently varied. Therefore, the linear inerter with a constant inertance is converted to the nonlinear inerter with a variable displacement-dependent inertance.

(28) For the designed displacement-dependent inerter device shown in FIG. 4, the working width of the piston, which is linearly related to the length of the helical path, is equal to (w/2) x, where the origin of coordinates is located on the center of the cylinder. Obviously, the piston must run between −w/2 and w/2, i.e., x∈[−w/2, w/2]. Therefore, it is needed to substitute (w/2)−x for w into Eq. (4) as follows:

(29) $\begin{array}{cc}B\left(x\right)=b_0\left(\frac{w}{2}-x\right)& \left(5\right)\end{array}$

(30) It indicates that the inertance at a given instant is an explicit function of the relative displacement between the terminals.

(31) It is easy to know that the relationship between displacement x and momentum p, which are the time integrals of velocity v and force F, respectively, defines the mechanical analog of a memristor, namely, the mem-dashpot (see FIG. 3). Consider a constitutive relationship between integrated momentum δ and displacement x, as shown in FIG. 3, i.e.,
δ={circumflex over (δ)}(x), with δ:=∫.sub.−∞.sup.tp(τ)dτ  (6)

(32) Differentiating the latter with respect to time yields

(33) $\begin{array}{cc}p=\frac{d\hat{\delta }}{\mathrm{dx}}\left(x\right)v& \left(7\right)\end{array}$

(34) By defining B(x)=d{circumflex over (δ)}(x)/dx, the displacement-dependent inerter shown in FIG. 4 can be described by the following equation:
p=B(x)v  (8)

(35) Suppose that we actuate the device with dimensions from Tab.1, using a sinusoidal velocity excitation v=Aω sin(ωt+π/2), and compare the characteristics of the device for different helix pitches. Considering the maximum working stroke of the device, it is assumed that A=0.05 m and ω=2π. The results are shown in FIG. 4.

(36) TABLE-US-00001 TABLE 1 Displacement-dependent inerter details. Description Value Piston diameter D 0.1 m Piston rod diameter d 0.012 m Helical channel radius r.sub.h 0.008 m Helix pitch P 0.04 m Piston width w 0.1 m Working stroke L 0.1 m Fluid density ρ 1000 kg m.sup.−3

(37) FIG. 6a shows that the inertance of the device shown in FIG. 4 is not a constant, but varies with the relative displacement between the terminals, which proves that the device is a displacement-dependent inerter. As can be seen in FIG. 6b, the relationship between momentum and velocity is two-valued everywhere except at the origin. This means if the memory elements are not considered, we will not define a proper relation for the curve shown in FIG. 6b, i.e., a single-valued mapping, between momentum p and velocity v. These difficulties are circumvented by modelling the displacement-dependent inerter as a mem-inerter, as obtained in Eq. (7), using the single-valued relationship between integrated momentum and displacement variable to define the displacement-dependent inerter as a mem-inerter (see FIG. 6c). In fact, pinched hysteresis loops as observed in FIG. 6b have been identified in the electrical domain as the fingerprints for a collection of circuit elements with memory. Therefore, according to the mechanical-electrical analogies, the displacement-dependent inerter device shown in FIG. 4 can be identified as a mem-inerter device. This means that the hydraulic mem-inerter device provided by the present invention is an implementation of the ideal mem-inerter element.

(38) FIG. 7a clearly shows the difference between the inerter and the mem-inerter. That is, the inertance of the inerter is a constant value, and the inertance of the mem-inerter is a variable value which is related to the relative displacement between the terminals. As can be seen in FIG. 7b, the inerter has the property that the applied force at the terminals is directly proportional to the relative acceleration between them, while the mem-inerter obviously differs from the inerter in the mechanical characteristics. As shown in FIG. 7c, the p-v characteristic curve of the inerter device is a straight line, while one of the mem-inerter device is a pinched hysteresis loop which have been accepted as the fingerprints of memory elements. It is visible that the two devices are essentially different. One is a common element and the other is a memory element. Similarly, the momentum integral and displacement characteristic curve shown in FIG. 7d also indicates that the two devices have different characteristics. Therefore, in terms of the displacement correlation of the inertance, mechanical properties and essential characteristics, the mem-inerter is essentially different from the inerter, and they are two different mechanical elements.

(39) The further modelling and testing demonstrated that the viscosity of the fluid provides a departure from ideal behavior, and flowing fluid may make a mem-inerter device produce a parasitic damping. This means the hydraulic mem-inerter device can be further modelled as an ideal mem-inerter element in parallel with a parasitic damping element.

(40) The following aspects illustrate the parasitic damping of the mem-inerter in detail by FIG. 4.

(41) Consider the hydraulic inerter device shown in FIG. 1, where a piston, a cylinder, a helical channel and a fluid with viscosity make up a simple viscous damper. According to the Hagen-poiseuille flow equation, the damping coefficient of the simple viscous damper can be obtained, i.e.,

(42) $\begin{array}{cc}c=8\pi \mu {l\left(\frac{A_1}{A_2}\right)}^2& \left(9\right)\end{array}$
where μ is the viscosity of fluid.

(43) Eq. (9) can also be represented in the form

(44) $\begin{array}{cc}c=\frac{8\pi \mu \sqrt{P^2+{\left(\pi D\right)}^2}}{P}{\left(\frac{A_1}{A_2}\right)}^{2}w& \left(10\right)\end{array}$

(45) For the displacement-dependent inerter device shown in FIG. 4, as described before, the length l of the helical path varies with the relative displacement between the terminals in the running process. Therefore, it can be known by Eq. (9) that the damping coefficient of the mem-inerter device is dependent on the relative displacement. In like manner, it is needed to substitute (w/2)−x for w into Eq. (10) as follows:

(46) $\begin{array}{cc}c\left(x\right)=\frac{8\mathrm{\pi \mu }\sqrt{P^2+{\left(\pi D\right)}^2}}{P}{\left(\frac{A_1}{A_2}\right)}^2\left(\frac{w}{2}-x\right)& \left(11\right)\end{array}$

(47) It indicates that the parasitic damping c(x) of the mem-inerter device at a given instant is an explicit function of the relative displacement between the terminals.

(48) Under the sinusoidal velocity excitation v=Aω sin(ωt+π/2) with A=0.05 m, ω=2π and μ=10.sup.−3 Pas, the damping characteristic curves of the mem-inerter device are shown in FIG. 8.

(49) FIG. 8a shows that the damping coefficient of the mem-inerter device is not a constant, but varies with the relative displacement between the terminals, which proves that the damping characteristic of the device is dependent on the relative displacement. It is well-known that the F-v curve of the linear damper is a straight line with a slope, while the F-v damping characteristic curve of the device is a pinched hysteresis loop as observed in FIG. 8b, which is identified as a typical fingerprint for a mem-dashpot. This means the device with the parasitic damping is a mem-dashpot. Since the F-v curve described above is not a single-valued mapping, the damping characteristics of the mem-dashpot cannot be defined by the relationship between the damping force F and velocity v. As can be seen in FIG. 8c, the F-x curve of the device is a single-valued mapping, and thus the damping characteristics of the mem-dashpot can be defined by the relationship between the momentum and relative displacement.

(50) In conclusion, the device provided by the present invention can be modelled as an ideal mem-inerter element. That is, the device is an implementation of the ideal mem-inerter element. Considering the viscosity of the fluid, the device provided by the present invention could produce a parasitic damping which is a damping with memory rather than a common damping. The mem-inerter device provided by the present invention is essentially different from the prior inerters device in the displacement correlation of the inertance, mechanical properties and parasitic damping characteristics. They are two different mechanical elements. From the characteristic curves, the mem-inerter device has better mechanical properties to control and counteract vibrational forces.

(51) The following aspects further illustrate the application of the hydraulic mem-inerter device as an adjustment and control valve of the inertance by FIGS. 9 and 10.

(52) In FIG. 9, when the hydraulic mem-inerter device is used as an adjustment and control valve of the inertance, the two openings 8 are respectively arranged on the ends of the cylinder wall, so that the fluid outside of the device can flows into one of the first openings and out from the other first opening of the first cylinder via the helical path. The setting principle of the openings 8 is not to be covered by the piston 3 (that is, the first openings 8 respectively arranged on the ends of the first cylinder wall are normally opened relative to the first piston 3). By continuously adjusting and controlling the relative displacement between the terminals of the device, in use, the length of the helical path and the mass of the fluid in the path can be changed to achieve continuous adjustment and control of the inertance.

(53) FIG. 10 is an embodiment of the application as an adjustment and control valve of the inertance, namely, an adjustable inerter device, comprising a hydraulic mem-inerter device 9, two hydraulic tubes 10 and a hydraulic cylinder 11. The hydraulic cylinder 11 includes a second cylinder 12 and a second piston 13, and the second cylinder 12 and the second piston 13 are the first and second terminals for connection, in use, to components in a system for controlling mechanical forces and independently movable. The two second openings 15 are respectively arranged on the ends of the second cylinder wall. Moreover, the setting principle of the second openings 15 is not to be covered by the second piston 13 (that is, the second openings 15 respectively arranged on the ends of the second cylinder wall are normally opened relative to the second piston 13). The two second openings 15 of the second cylinder 12 respectively connect with two first openings 8 on the first cylinder 1 by the hydraulic tubes 10. The whole adjustable inerter device is filled with a fluid 7.

(54) For the adjustable inerter device shown in FIG. 10, let S.sub.1 be the effective cross-sectional of the second piston 13. According to Eq. (5), the inertance between the terminals (the second cylinder 12 and the second piston 13) can be calculated when an instant or a position of the first piston 3 of the mem-inerter device 9 are given, i.e.,

(55) $\begin{array}{cc}{B}_v\left(x\right)={\left(\frac{S_1}{A_1}\right)}^{2}B\left(x\right)& \left(12\right)\end{array}$

(56) According to Eq. (11), the parasitic damping coefficient between the terminals (the second cylinder 12 and the second piston 13) can be calculated at this time, i.e.,

(57) 0$\begin{array}{cc}{c}_v\left(x\right)={\left(\frac{S_1-A_2}{A_1}\right)}^{2}c\left(x\right)& \left(13\right)\end{array}$

(58) Equations (5) and (12) indicate that the inertance provided by the adjustable inerter device continuously varies with the relative displacement between the terminals of the mem-inerter device 9. In other words, the inertance can be continuously adjusted and controlled by continuously changing the relative displacement between the terminals of the mem-inerter device 9.

(59) Equations (11) and (13) indicate that the parasitic damping coefficient provided by the adjustable inerter device 9 continuously varies with the relative displacement between the terminals of the mem-inerter device 9, In other words, the damping coefficient can be continuously adjusted and controlled by continuously changing the relative displacement between the terminals of the mem-inerter device 9.