JP2010511848A - Rolling bearing and seismic isolation device equipped with the rolling bearing - Google Patents

Abstract

A roller bearing particularly suitable for use in a seismic isolation device is provided.
The roller bearing is a slide plate having a substantially circular bottom surface intended to roll on the layer of balls, and a substantially ring-like shape surrounding the bottom surface with an inner knife-like edge. And a frustum-shaped ring-shaped gap space for receiving and recirculating the balls that are open toward the bottom surface.

Description

  The invention, in its broadest aspect, relates to the technical field of elements for reducing and controlling the friction between two objects, in particular to the field of so-called ball and roller bearings.

  More particularly, the present invention relates to a roller bearing suitable for use in, but not limited to, a heavy duty transport assembly and kinematic seismic isolation device, particularly with friction switching control. .

  Therefore, in the following, for purposes of illustration, the roller bearing according to the invention will be described in the field of earthquake prevention, in particular in the field of seismic isolation devices, but the invention is not limited thereto.

  As is well known, structures that can withstand severe natural phenomena such as earthquakes (especially undulating earthquakes) in the field of buildings and broadly construction and overcome such natural phenomena without causing damage. There is a particular need to provide

  In order to meet such needs, the prior art provides construction methods that use so-called seismic isolation devices.

  Seismic isolation devices do not allow superstructures (residential constructions such as buildings, apartments, houses, and similar structures, or structures of the type such as industrial plants and various infrastructures) during seismic events or earthquakes. It is a special device that can be isolated from the movement of the ground where the superstructure is located.

  Among the various types of seismic isolation devices, the seismic isolation device, most specifically known as an elastoplastic damper and structural energy removal system, has advantages, but presents several drawbacks.

  In fact, the above-mentioned seismic isolation devices can prevent, for example, building collapses in the event of an earthquake, but possibly guarantee adequate protection for people present in such buildings in the event of an earthquake. Can not.

  Another technical solution provided by the prior art consists of using a so-called kinematic seismic isolation device, which in effect isolates the superstructure from the ground. As an insulating element, it is characterized by the fact that a ball or ball bearing or roller bearing can move on a surface called a sliding surface (sometimes defined as a rolling or sliding surface).

  In practice, such a seismic isolation device is interposed between the ground and the superstructure as a kind of slider that allows the superstructure to move on a rolling surface integral with the ground with low friction. Function.

  This type of seismic isolation device is also advantageous in that it provides a high insulation capacity consisting mainly of reducing the horizontal component of the relative acceleration transmitted to the superstructure to a value corresponding to the coefficient of rolling friction. There are some drawbacks.

  Specifically, the seismic isolation device that constrains the rolling of an insulating element made of a ball between a flat surface or a spherical surface has both a Love wave and a Rayleigh wave at the same frequency, that is, there is rotational translation. Then, when the event of the earthquake ends, the final relative position of the ball no longer coincides with the initial position before the occurrence of the vibration.

  In this case, in some cases, the ball may come off the seat provided for the ball, adversely affecting the integrity of the superstructure.

  The above drawbacks are referred to as kinematic discrepancies and are generally between the cap surfaces (one surface corresponds to the above-mentioned sliding surface integral with the ground and the other corresponds to the rolling surface of the same bearing). All prior art seismic isolation devices that use balls that roll are subject to kinematic discrepancies.

  Although compound linear slide isolators, such as compound one-way recirculating bearings or ball isolators, are known in the art to prevent kinematic discrepancies, they do not provide insulation from vertical torsion caused by Love waves. Impossible.

  Furthermore, with regard to rolling surfaces, it should be noted that when such rolling surfaces are flat or spherical, the seismic isolation device is critically affected by wind as follows. That is, in order to be stable in the presence of strong winds, it is necessary to provide an auxiliary centering and damping element in such a seismic isolation device, which means that an additional transmission element is provided, which is unavoidable In particular, the advantage of high rolling ability on the ball is negated.

  In particular, centering elements that can be provided with various degrees of elasticity inevitably have resonance frequencies that lie within the strong spectrum of earthquakes.

  As a result, damping elements are required, but such damping elements are characterized in that the superstructure is isolated from very high frequencies, but as a whole undergoes vibrations of considerably lower frequencies.

  Furthermore, in systems with a plurality of seismic isolation devices of the type described above, due to the fact that the center of thrust of such system interaction with the ground is not always located on the vertical axis of the center of gravity of the superstructure. There are problems related to mechanics. That is, the resultant force of the transmitted force has a non-zero vertical moment with respect to the center of gravity of the superstructure itself.

  It should be noted that a seismic isolation device having a conical slide surface is not subject to the above-mentioned drawbacks due to wind, but can occur when a ball or rolling element passes through the center of the conical surface during an earthquake. There are even more serious disadvantages associated with impulse peaks.

  In this case, the reaction impact (rebound) can occur in the superstructure with greater vertical and horizontal instantaneous accelerations than caused by the seismic event itself, resulting in inevitable damage to the rolling surface. .

  Thus, in practice, a rolling surface of the type described above is considered impractical.

  Furthermore, all ball-type seismic isolation devices provided by the prior art have a limited surface area of contact between the insulating element and the sliding surface, and such limited contact surface area has a long period of time. Due to the large pressure applied over the time, i.e. exposed to high load values, it has the further serious drawback of so-called cold welding.

  In other words, as noted above, the resistance of superstructures to seismic waves presents a substantially unresolved problem in the construction field so far, where the prior art still provides only inadequate technical solutions. Yes.

  Accordingly, a kinematic seismic isolation device capable of overcoming the above-mentioned drawbacks of the prior art, in particular a seismic isolation device of the type described above, especially from the ground of the superstructure with respect to friction in the event of a undulating earthquake. It would be desirable to provide a seismic isolation device with an insulating element that can guarantee almost complete insulation while being substantially unaffected by wind in the absence of seismic events.

  The present invention is a roller bearing type insulation means for reducing and controlling the friction between two objects, which can overcome the above-mentioned drawbacks, and is a first that moves relative to a second object. Insulating means are provided that can provide almost complete insulation of the object.

Accordingly, within the scope of some embodiments, the present invention provides:
A slide plate having a substantially circular planar or spherical cap-like bottom surface intended to roll on a layer of balls;
A substantially ring-shaped boundary element surrounding the bottom surface having an inner knife-like edge, and a cone for receiving and recirculating the ball open towards the bottom surface The present invention relates to a roller bearing having a trapezoidal ring-shaped gap space.

  In another embodiment, the present invention is a transport assembly for switching friction from sliding friction to rolling friction as well as rolling friction to sliding friction, for moving loads (even heavy loads) It relates to a transport assembly which is particularly suitable and preferably comprises a roller bearing of the type described above.

  In yet another embodiment, the present invention is a kinematic seismic isolation device comprising a transport assembly for switching friction from sliding friction to rolling friction and rolling friction to sliding friction, such as The present invention relates to a seismic isolation device in which the transport assembly comprises a roller bearing of the type described above.

  Further features and advantages of the present invention will become more apparent from the detailed description set forth below with reference to the accompanying drawings, which are by way of example only and not intended to limit the invention.

The perspective view which has cut | disconnected some roller bearings by this invention. The exploded view of the bearing of FIG. FIG. 2 is a smaller schematic view of the cross section of the bearing of FIG. 1. FIG. 2 is a smaller view of the top view of the ball flow of the bearing of FIG. 1 is a schematic cross-section and elevation of a vertical axisymmetric seismic isolation device according to the present invention comprising a transport assembly for switching loads according to the present invention. Schematic which shows the group which consists of the several seismic isolation apparatus by this invention interposed between the superstructure and the ground. Schematic which shows the group which consists of the several seismic isolation apparatus by this invention interposed between the superstructure and the ground. The figure of the cutting force / relative displacement of the seismic isolation device by this invention. Typical time diagram of the force Ft transmitted by the ground to the superstructure via the seismic isolation device of the present invention and the force F1 acting vertically on the ball bearing according to the present invention. A typical diagram of earthquake events. FIG. 4 is a relative diagram of acceleration and displacement transmitted to an upper structure through a seismic isolation device according to the present invention by an earthquake event. 1 is a schematic view of an automatic inertial motion seismic isolation device according to the present invention in several stages of operation. 1 is a schematic view of an automatic inertial motion seismic isolation device according to the present invention in several stages of operation. 1 is a schematic view of an automatic inertial motion seismic isolation device according to the present invention in several stages of operation. 1 is a schematic view of an automatic inertial motion seismic isolation device according to the present invention in several stages of operation. 1 is a schematic view of an automatic inertial motion seismic isolation device according to the present invention in several stages of operation. 1 is a schematic view of an automatic inertial motion seismic isolation device according to the present invention in several stages of operation. 1 is a schematic diagram of a seismic isolation device for external control operation according to the present invention in several stages of operation. FIG. 1 is a schematic diagram of a seismic isolation device for external control operation according to the present invention in several stages of operation. FIG.

  1-3, according to a first aspect of the present invention, the entire element for reducing and controlling the friction between two objects (hereinafter referred to as a roller bearing or simply a bearing) 1.

  The bearing 1 is the type used in combination with a ball, and when relative movement occurs between the two objects, the two objects are used to reduce or eliminate friction between the two objects. It is intended to be interposed in between and, according to the present invention, is particularly suitable for use in seismic isolation devices, as will be described in more detail below.

According to the invention, the bearing 1 is basically
A slide plate 2 having a substantially circular flat or spherical cap-like bottom surface 3 so as to roll on a dense layer or a substantially dense layer (rolling layer) of the balls 4;
The boundary element 5 of the layer of balls 4 which is substantially ring-shaped around the bottom surface 3 and has a knife-like edge 6 inside;
A ring-shaped gap space 7 in the shape of a truncated cone that opens toward the bottom surface 3 and communicates with the bottom surface 3 for receiving and recirculating the balls;
It has.

  Specifically, the balls 4 in the above-described ball layer are substantially the same size and, as will be described in more detail below, one of the two objects intended to reduce friction (shown in the above figure). (But not referred to as a first object) or a slide surface integrated with such a first object.

  Such a sliding surface may be a flat or spherical cap shape, in which case it is concentric with the spherical cap-shaped bottom surface 3 of the sliding plate 2 of the bearing 1.

  Further, the bearing 1 includes a predetermined number of passages 9c of appropriate predetermined dimensions for introducing the balls 4 into the frustoconical ring-shaped gap space, as will be described in more detail later. The passage 9 c extends substantially in the axial direction with respect to the frusto-conical ring-shaped gap space 7, and is disposed at a position substantially opposite to the bottom surface 3 of the bearing 1.

  As shown in the above-mentioned figure, with particular reference to the example of FIG. 2, according to an embodiment of the invention, the above-mentioned slide plate 2 comprises an oblique substantially frustoconical side 8. It is basically a frustoconical object.

  The side surface 8 extends between the aforementioned bottom surface 3 and the cylindrical ring-shaped part 9 on the opposite side, and advantageously, a chamfered edge 9 b is formed between the side surface 8 and the bottom surface 3. Is done.

  Further, the bearing 1 has the cover cap 10 of the slide plate 2 arranged at a predetermined distance from the side surface 8 so as to define the above-described gap space.

  It should be noted that the slide plate 2 is formed in such a manner that the cap 10 integrally forms a substantially rigid system in the cylindrical ring-shaped portion 9 by a known type of fixing means such as a screw 9d. To be combined.

  Advantageously, in the circular ring-shaped part 9, ie in the vicinity of the corresponding end of the side surface 8 described above, the slide plate 2 and the cap 10 define an annular groove 9 a that defines the upper part of the gap space 7. Yes. The gap space 7 communicates with the external space by the above-described passage 9c (in the example shown, represented by two through holes provided in the cap 10).

  In contrast, as described above, the other end of the gap space 7 is fully open and communicates with the bottom surface 3 of the slide plate 2, and thus communicates with the rolling layer formed by the balls 4. Yes.

  The boundary element 5 of the layer of the ball 4 described above is preferably restricted with respect to the rotation with respect to the cap 10 and can be displaced in the axial direction.

  Therefore, in the above-described embodiment of the bearing according to the present invention, the above-mentioned frusto-conical ring-shaped gap space 7 is configured to be laterally defined between the side surface 8 of the slide plate 2 and the cap 10, and more particularly As will be described later, an actual chamber for receiving and recirculating the balls 4 is formed.

  Preferably, the bearing 1 is provided with a receiving seat 11 at the end opposite to the bottom surface 3 of the slide plate 2. As will be described in more detail later in this specification, the receiving seat 11 is the other of the two objects (not shown in the figure, but not shown in the figure) that is intended to reduce friction during the relative movement described above. Of the bearing) or is intended to engage another object integrated into such a second object, It is intended to accommodate predetermined thrust means for typical vertical movement.

  As shown in the example of the figure, when the above-mentioned receiving seat 11 is provided on the slide plate 2 in this bearing, the cap 10 is substantially similar for access to such receiving seat. A width related passage 9e is provided.

  In practice, the bearing according to the invention is arranged so as to rest on the aforementioned layer of balls in operation, such a layer of balls lying substantially in contact with the sliding surface of the first object. While being closed at the perimeter by the element, a suitable number of other balls are accommodated in the gap space described above.

  Note that the rolling layer composed of the balls 4 is always densely shown in the figure, but this dense state is actually automatically formed when the bearing is used. This is because the boundary element is a substantially ring-shaped element, leaving the bottom of the bearing “open”.

  If a relative movement occurs between the first and second objects described above, or a relative movement occurs between other objects integrated into the first and second objects described above, then in fact the second In a bearing according to the present invention integrated into the object, substantial recirculation of the ball and closed flow movement can occur in all directions of the slide, as will be described in more detail below.

  For example, when the second object moves in parallel with the first object at the speed Uc, the relative movement of the above-described ball layer (rolling layer) at the ball speed Us1 = 1 / 2Uc. Exists.

  Specifically, the ball moves between the rolling surface of the first object and the bottom surface of the bearing slide plate until it reaches the boundary element.

  The boundary element carries the ball emanating from the rolling surface (i.e. rolling layer) of the first object into the gap space, i.e. in the opposite direction to the movement of the second object (bearing), by means of the inner knife-like edge described above. Carry.

  In addition, the knife-like edge of the boundary element also serves to help access the first object's rolling surface (ie, the rolling layer) for other balls coming from the clearance space (recirculation chamber). These balls replace the balls that are carried into the interstitial space as described above in a substantially opposite portion of the moving ball layer and form the closed flow recirculation described above.

  The above brief description is illustrated in the example of FIG. In FIG. 4, the flow line (indicated by A) of the ball (rolling layer ball) under the load of the second object, and the flow of the ball in the gap space with velocity Us2 = 3 / 2Uc. The line (indicated by B) is schematically shown in plan view.

  Basically, when a bearing is used, the clearance space of the bearing according to the present invention is already partly occupied by a predetermined appropriate number of ball sets, even in the absence of motion (rolling). With the gap space appropriately dimensioned with respect to the size of the ball, the layer of the ball between the rolling surface of the first object and the bottom of the sliding bearing (rolling layer) During this time, it remains virtually in a dense state.

  In fact, it is unlikely that the ball will come into contact earlier due to elastic collisions between the balls caused by the rolling of the first object at the thrust of the balls leaving the rolling surface and rolling freely in the gap space. Thus, sliding friction between two adjacent balls is unlikely to occur.

  The shape of the bearing must be such that no ball can simultaneously contact the bottom of the slide plate and one between the boundary element and the bearing cap.

  The values of the static and dynamic rolling friction coefficients of the bearing are attributed to both the ball on the rolling surface (rolling layer) of the first body and the free ball in the clearance space as a whole.

  The contribution of the clearance space to the ball friction is due to the flow of carrier energy when lifting the ball in the clearance space, which is converted into heat due to collision.

  While not limiting the scope of protection of the present invention to any theory, in practice, the operation of this bearing is the same, constrained to rotation between two relatively moving surfaces, as summarized below. It takes advantage of the characteristics of (or nearly identical) ball pairs.

  The load capacity of the ball layer and the relative shrinkage under load do not depend on the radius of the ball, but on the total cross section at the center. Also, the static and dynamic rolling friction coefficients are substantially independent of the ball radius, so this bearing basically has a large load capacity and has a very low rolling friction coefficient. Guarantee.

  The center-to-center distance of the ball is constant and does not change with translation and rotation, so the center of the ball moves in a dense manner.

  Advantageously, the lower limit of the radius of the ball is basically determined by the degree of tolerance of the reproducibility of the ball itself.

  More advantageously, the bearings of the present invention do not suffer from the disadvantages described above as kinematic inconsistencies that adversely affect the double rolling surface ball bearings provided by the prior art.

  As previously observed, in such a bearing, the ball rolls between planes or spheres, and the final relative position of the ball in the case of an overlap of relative parallel and spheroidal motion (rotational translational motion). It does not coincide with the initial position and has an undesirable effect on the protection of the superstructure. As already mentioned, this does not occur when the bearing according to the invention is used in a kinematic seismic isolation device.

  According to a second aspect of the invention, a friction-switching transport assembly for the movement of luggage is provided as schematically shown in the example of FIG. 5, in the example of FIG. A transport assembly is employed in a seismic isolation device that is used to insulate the superstructure from the relative movement of the ground on which the superstructure is located.

  In practice, there is provided a transport assembly (indicated generally at 100) having a controlled switching from sliding friction to rolling friction and vice versa, such a transport assembly. Is particularly suitable for transporting or moving loads (even heavy loads), as occurs when the above ground / superstructure insulation is required.

  According to the present invention, the above-described controlled friction switching type transport assembly 100 has a high adhesion coefficient (sliding friction) capable of supporting a predetermined load (Fc) including a heavy load in an idle state (stationary state). It has an idle support 101 and a rolling element 102 housed inside the idle support (101). The load described above is released to the rolling element 102 by a device or mechanism that can produce a relative thrust (F1 = FC) between the idle support 101 and the rolling element 102 that switches to rolling friction.

  Thus, the rolling element 102 must be able to move freely in a substantially vertical manner inside the idle support 101 over a limited predetermined length section of about 1 mm.

  According to the present invention, the friction switching type transport assembly 100 is fully functional by the load switching device 100a (or the friction switching device). The load switching device 100a is basically located on the idle support 101, functions as an actual support for the load Fc, the bridge element 103, the thrust means 105 acting on the rolling element 102, and a predetermined And propulsion means 106 capable of producing a force F1 = Fc to the thrust means described above over a period of time.

  This switching device is advantageously controlled by dedicated on / off means 107.

  Actually, the bridge element 103 functions as a support portion for the load Fc described above, and transmits this load itself to the idle support 101 on which the bridge element 103 is substantially mounted.

  In contrast, the force generated by the propulsion means 106 is transmitted to the rolling element 102 by the thrust means 105 described above.

  The above-described exchange, ie the thrust (F1) to the rolling element corresponding to the load Fc can be obtained by mechanical or hydraulic means, preferably by hydraulic means.

  Preferably, the rolling element 102 described above is a roller bearing according to the description outlined above, i.e. a ball recirculating omnidirectional bearing placed on a layer of rolling balls, although the possibility of providing known types of bearings. Is not to be excluded.

  In practice, it is important that the load change, ie the friction change from slide to rolling, and the opposite change occur quickly between the idle support and the rolling element (and vice versa). is there.

  Additional features of the friction switching transport assembly 100 described above are described below with particular reference to use in a kinematic seismic isolation device that represents a further aspect of the present invention. The entirety of such a base isolation device is indicated by 200 in the examples of FIGS.

  The term “seismic isolation device” is used herein to refer to a special case, as described above, that can insulate the superstructure 500 from the motion of the ground 600 carrying the superstructure during an earthquake event or earthquake. Is used to point to various devices.

  FIGS. 6 and 7 described above show a method of installing a plurality of seismic isolation devices arranged on a column below each pillar foundation having an appropriate height to enable maintenance.

  In particular, in the example of FIG. 6, a plurality of seismic isolation devices are arranged on the slide base 201a parallel to the ground, and the arrows indicate the height between the positions of the seismic isolation devices in the presence of possible ground rotation. Only the form of deformation applied to the superstructure due to the difference is shown.

  The illustrated arrangement allows the horizontal and vertical acceleration components to pass and prevents the transmission of horizontal and vertical angular acceleration.

  In contrast, in the example of FIG. 7, a plurality of seismic isolation devices are arranged concentrically on the slide base 900. The seismic isolation device allows only vertical linear acceleration to pass and allows the reduction of all three angular acceleration components.

  In either case, the center of rotation C (the center of the concentric base) can be much higher and in any case can be located above the center of gravity of the superstructure 500, so that the cap-shaped slide base is actually Can be replaced by a flat surface, possibly slightly elliptical to provide vertical rotation stability to the superstructure.

  The seismic isolation device 200 basically includes a slide base 201 of the type described above and the load switching transport assembly 100 described above. The load switching conveyance assembly 100 has a large friction coefficient with the slide base 201, is accommodated inside the idle support 101 attached to the slide base 201, and is displaced in the vertical direction inside the idle support 101. Omnidirectional roller bearing 102 located on the layer of the ball 4 and indicated generally by 100a to transmit the load of the superstructure 500 from the idle support 101 to the bearing 102, and further The load switching device described above that transmits in the opposite direction is provided. Furthermore, the seismic isolation device 200 includes a fixed header 206 to the upper structure 500 as shown in the examples of FIGS.

  Note that the switch from sliding friction to rolling friction substantially eliminates wind problems, thus eliminating the need to use a centering element having an appropriate predetermined force in the seismic isolation device.

  Regarding the above-mentioned slide base, such a slide base is usually made of reinforced concrete, and preferably has a cap shape with a large radius of curvature.

  As an advantage, in the case of a large radius of curvature (Rc), the resonance period of the seismic isolation device of the present invention is very long.

  The slide base 201 is made in one piece with the ground 600 and advantageously has a steel sheet whose thickness is preferably the dimension of the ball 4 used for the bearing 102 and is indicated by 205 in the example shown. Or covered with other suitable metals or metal alloys. Such a technical solution is preferably employed with the aim of avoiding concrete collapse which can be caused by a strong point pressure during contact between the ball and the concrete itself.

  By using a relatively small ball, it is possible to reduce the thickness of the sheet 205 that becomes an actual slide surface when it is provided so as to cover the slide base 201. Therefore, the weight and cost of the entire seismic isolation device Can be reduced.

  As already mentioned, the bearing 102, which is omnidirectional and slides vertically within the low friction idle support 101, does not suffer from the kinematic discrepancy as described above.

  In fact, the balls that can be found between the rolling surfaces (steel sheet covering the slide base and the bottom of the bearing) at the end of the earthquake event are partially or fully It can be a ball housed in a space (which is the bearing recirculation chamber).

  The load from the idle support 101 is transmitted to the bearing 102, and vice versa, so the friction coefficient is the friction coefficient of the adhesion of the idle support 101 to the slide base 201 (with or without a metal sheet). According to the present invention, the load switching device 100a that converts the rolling friction of the bearing 102 on the slide base 201 to the rolling friction is of the so-called inertia automatic operation type that can obtain the operating energy from the earthquake event itself. It may be of an external control operation type with an autonomous energy source.

  In the case of an inertial automatic motion seismic isolation device (IA), a coefficient called a first decoupling coefficient that is substantially the same for all seismic isolation devices of a complex system including a plurality of seismic isolation devices of this type, It is necessary to set in advance in such a manner that all the seismic isolation devices operate synchronously and all the effects of non-earthquake thrust are removed. The manner in which this can be achieved will be described later.

  Furthermore, the characteristic and advantageous feature of the automatic inertial motion isolation device is that the seismic isolation device is moved while the superstructure is stationary, so that there is a degree of freedom of vertical axis rotation. It is extremely useful for avoiding cold welding due to long-term pressure and plastic deformation of the rolling surface located inside. In contrast, the embodiment of the seismic isolation device with external control operation does not require the setting of the first desorption coefficient, does not have an internal rolling surface, and simultaneously with the above-mentioned self-supporting energy source, It is equipped with an on-site or remote acceleration sensor in a manner that enables pre-arrival operation.

  A combination operation of the switching device obtained from a combination of the above two types of operations is also possible.

  The main condition is that, in the case of automatic operation, the specific threshold characteristic described above, which is substantially the same for all seismic isolation devices of a system comprising a plurality of seismic isolation devices, is in accordance with the invention according to switching and temporal hysteresis operation. As well as the switching time.

  In any case, along with the fixed header 206 to the superstructure 500 described above, the seismic isolation device according to the present invention further comprises a subheader with a ball joint 207 on which the header 206 is mounted, It coincides with the upper part of the bridge element 103 described above.

  The above-mentioned configuration, ie, the “joint disconnection” of the header 206 obtained by the joint of the sub-header (bridge element 103) or the ball joint 207, compensates for the variation in inclination during the movement that occurs in the case of a rolling-based spherical surface. Prevents torsional moments on the bridge element 103 and the bearing 102.

  Thus, the support surface between the header 206 and the sub-header having the ball joint 207 is preferably made in the shape of a spherical cap that has a slightly different radius and is as large as possible to increase the same contact surface. The

  As already indicated, the load switching device 100a described above is basically capable of generating a bridge element 103, thrust means 105 acting on the bearing 102, and a force F1 equal to the load Fc over a suitable time period. The seismic isolation device according to the present invention having the propulsion means 106 and having the friction switching device of the inertia automatic operation type as described above and the seismic isolation device according to the present invention having the external control drive type friction switching device. Further details will be described below with reference to the examples of FIGS. 12-17 and FIGS. 18 and 19, respectively.

  In the case of automatic operation, the seismic isolation device of the present invention comprises a piston arranged to form a ring (in other words, preferably four or more inertial operation pistons 301, in this particular case the base 201 The idle support 101 provided with a bell 302 attached to a metal sheet 205 covering the metal sheet 205) and an element identified in a cylindrically symmetric casing 303. The cylindrically symmetric casing 303 is actually positioned on the bell 302 inserted into the casing element 303 with the vertical axis positioned upward and through the outer annular surface. ing.

  Between the casing 303 and the bell 302, contact at the center between the casing and the bell is avoided, and the load Fc is concentrated on the bell 302 in an annular manner (and therefore under load). A central clearance space 303a having a thickness suitable for absorbing the elastic deformation of the upper part of the casing and distributing the load itself evenly to elements (particularly, the layer of the small balls 308) is defined. As will be described in more detail later, an outer circumferential annular space (herein also referred to as a first chamber 304) that communicates with the piston 301 via the corresponding first pipe 306 is defined. .

  In this particular case, the bearing 102 is housed inside the bell 302 of the idle support 101.

  In detail, the bearing 102 inside the bell 302 is located on the layer (rolling layer) of the balls 4 arranged on the slide base 201 (in particular, the seat 205) as described above, while the bearing 102 A piston portion 302a of the bell 302 is engaged with the receiving seat 11 (of the above-described type), and a relative clearance space called a second chamber 305 is defined between the receiving seat 11 and the piston portion 302a. .

  The second chamber 305 communicates with the first chamber 304 by a relative second pipe 307 as shown in the examples of FIGS.

  Regarding the above-described pistons, they are accommodated in the bell portion 302 of the idle support 101 in an annular manner, while the casing 303 is accommodated immediately below the above-described bridge element 103, and the bridge element 103 is the bridge element itself. The above-mentioned piston 301 is contacted via a corresponding dedicated bracket element 103a (which functions as a piston driving element).

  Between the casing 303 and the bridge element 103 (subheader), a first desorption acceleration provided when the bridge element 103 designs the seismic isolation device by a highly friction-free movement on the casing 303. The layers of small balls 308 (ie, small diameter balls) described above are arranged in such a way that they can slide freely in all directions over the section of maximum width δ depending on (first desorption coefficient) and time hysteresis. Has been.

  Accordingly, a hydraulic “circuit” is provided in the switching device described above. The hydraulic “circuit” enables the switching of friction by the above-described oil piston 301 supplied by a common tank 320 (the above-mentioned propulsion means as a whole), and in particular is inflatable, and the first pipe 306 The first chamber 304 that is in communication with the piston 301 via the second chamber and the second chamber that is also inflatable and is in communication with the first chamber 304 via the second pipe 307. 305.

  The hydraulic circuit described above is filled with oil, has no air bubbles, does not leak, in other words, is watertight, and thus provides a special gasket where needed according to the experience of those skilled in the hydraulic system and circuit be able to.

  A valve 310 is arranged upstream of the first chamber, i.e. between the piston 301 and the first chamber 304, allowing a rapid flow of oil sent by the piston 301 towards the first chamber, and The very slow outflow described in detail below determines the return time of the seismic isolation device of the present invention in the sliding friction state.

  The above-mentioned second pipe 307 connecting the first and second chambers has a first channel 311 and a second channel arranged at slightly different heights substantially at the entrance to the first chamber. It has a branch that determines 312.

  As can be seen in the enlarged detail of the example of FIGS. 12-17, the first channel 311, which is arranged lower than the second channel 312 and has a limited cross section, is located between the first and second chambers. The second channel, which is much larger in cross-section, while ensuring constant fluid communication, is not always in communication with the first chamber 304.

  In practice, in an idle or stationary (no seismic activity) state, a load (Fc) of the superstructure 500 is applied to the idle support 101, more specifically to the casing 303, which in turn applies this load to the bell. To 302, and possibly to a slide base 201 covered by a steel sheet.

  Under such maximum load conditions (sliding friction), the thickness of the first annular chamber 304 described above is defined by a respective portion of the bell 302 and casing 303 that are substantially in contact with each other. Minimal or absent in that only lubricating oil can be present between the walls of the chamber.

  The bottom region of the first chamber is indicated by S1.

  In contrast, the thickness of the second chamber 305 is such that the wall of the casing 303 and the wall of the bell 302 are not in direct contact with each other, and this second chamber (bottom area is indicated by S2). A certain amount of oil is supplied to fill.

  In any case, the entire hydraulic circuit as described above is filled with oil without bubbles and is substantially free of pressure.

  In such a situation, as shown in the example of FIG. 12, there is a position defined as the center of the switch device. The switching device has an amount of oil corresponding to the filling of the thickness indicated by crp> δ in each drive piston 301 and is connected to the respective bracket element 103a (and hence the bridge element 103) via the relative drive pin 103b. In contact

When the number of pistons 301 is N, the number of pistons moved by the thrust of the relative bracket element 103a is N / 2, and each of these pistons is displaced in proportion to cos (α), Where α is the angle between the direction of acceleration of the ground as and the direction of the piston's own axis. Therefore, the total number of moving pistons corresponds to a single piston of stroke crp and cross section Sp = (N / 4) ^* sp, where sp represents the cross section of each piston.

  When the above-described ground acceleration as begins, ie during an earthquake event and seismic wave propagation, a relative force Fs acts on the corresponding moving piston 301 having a thickness crp = δ and a cross-section Sp, and Fs ≧ (Fc / S1) When Sp, the compression of the moving piston oil begins and the oil passes through the first pipe valve 310 to the first chamber (which is the only chamber that can expand at this moment), and as a result The casing 303 is lifted.

  At this stage, the bell 302 is still supporting the load Fc through the oil under pressure in the second chamber, so the friction is still a sliding type friction.

  When the value of the first desorption (FIG. 13) has not yet been reached, the narrowness of the first connection channel 311 between the two chambers may lead to a decrease in the first chamber to the second chamber. The direct and rapid flow of oil is hindered, so the oil pressure in the second chamber rises very slowly compared to the increase in pressure in the first chamber, so that the first chamber is in the first chamber. The top surface expands until it reaches the height of the second channel 312 having a significantly larger cross-section than the first channel 311.

  At this stage, the thickness of the second chamber remains substantially unchanged and oil flows freely towards the second channel 312 of appropriate cross-section towards the second chamber 305.

  In practice, before reaching the value of the first desorption, the first chamber expands until it reaches the opening of the second channel 312 which is at a higher height than the first channel, so that From the second channel 312, oil can flow into the second chamber at a higher rate.

  As soon as the volume of oil in the second chamber 305 reaches a value necessary for switching the load, the above-described desorption and rolling start.

  It should be taken into account that due to the elastic properties of materials exposed to high pressures, a finite but not infinitesimal amount of oil is required to reach a defined pressure differential value.

  The number and diameter of the pistons 301 and the stroke of the bracket elements determine the maximum amount of oil that is supplied to the first pipe and thus the first and second chambers.

In addition, the above-mentioned common that the moving piston 301 is disposed at an appropriate position and has an effective volume equivalent to the total volume Vc (Vc = Sp ^* crp) of the oil moved by the moving piston during inertial compression. Hydraulically parallel by an annular pipe 310b connected to the tank 320.

  The tank 320 is provided with a movable diaphragm 320b that separates the oil from suitable means such as liquid propane under saturated vapor pressure, thereby rolling to avoid the phenomenon of kinematic mismatch of the layers of small balls 308. In this case, the piston is returned to its initial position, and therefore the oil can be kept under sufficient pressure to return the bridge element 103 to its central position.

  In particular, the movable diaphragm described above should be placed as close as possible to the final stroke of the common tank in such a way as to prevent further increase of oil in the tank itself at the start of the switching phase.

  Instead, the example of FIG. 14 shows the state of the maximum displacement of the bracket element, and the first detachment in the maximum load state Fc corresponds to this.

  When Mc indicates the mass located on the casing 303 and g is the acceleration of gravity, the following formulas 1 and 2 are obtained.

  Thus, the first detachment state occurs when Fs reaches and exceeds the overall frictional force value due to the bell slide contribution and the bearing rolling contribution. Are given by Equation 3 and Equation 4, respectively.

  Here, Crad and Cvol are the friction coefficients of sliding and rolling, respectively, and P2 corresponds to the hydraulic pressure of the second chamber.

  Therefore, the acceleration (as) pd of the first desorption is the following Expression 5 and is obtained from the following Expression 6.

  According to the present invention, when considering the number of digits, (as) pd ≈ Sp / S2, which does not depend on the friction coefficient which is very uncertain, the load mass Mc and thus Fc, and is seismically isolated. It is observed that it depends only on the configuration features of the device, i.e. only on the specific internal shape of the seismic isolation device.

  In this manner, complete stability of the superstructure located on the seismic isolation device having the same shape is ensured in the event of an earthquake, also from a dynamic point of view.

  Once the first desorption acceleration is exceeded, rolling begins on the rolling layer, the pressure on the moving piston 301 is canceled, the force Fc is substantially disabled, and the valve 310 described above is applied to the piston 301. Prevents sudden return of oil. Thus, once desorption occurs, Fc remains added and is supported by the oil present in the first and second chambers.

  The bell 302 receives a downward thrust due to the oil pressure in the first chamber and an upward thrust due to the oil in the second chamber.

  If the horizontal cross section of the first chamber 304 is dimensioned slightly smaller than the horizontal cross section of the second chamber 305, the load is substantially the same (excluding the specific gravity of the bell) and the pressure P1 of the first chamber 304 Becomes larger than the pressure P2 of the second chamber 305. Therefore, the flow of oil from the first chamber to the second chamber via the second pipe 311 during rolling continues after the thrust of the piston stops. As a result, it is ensured that the coefficient of friction passes from a value of the first desorption corresponding to about 0.1 to 0.2 to a value corresponding to 0.002 to 0.005 of pure rolling. .

  This provides the necessary hysteresis to ensure that the switching occurs in a perfect manner.

  In practice, if the difference ΔS between the two chamber cross-sections is very small, the weight of the bell itself is adjusted so that the bell slides on a slide base that determines the frictional force corresponding to Equation 7 below. Acts as a valve.

  Note that the bell rises when the second member of the above relationship is negative, that is, when the weight of the bell is negligible. However, any slide will generate a friction force of the degree of rolling friction of the bearing, and therefore will not affect, considering the number of digits (bell weight) / Fc.

  Furthermore, the closing of the valve 310 during the rolling phase leaves the bridge element 103 free to move with respect to the casing 303 and lacks the centering force of the moving piston 301.

  The kinematic discrepancies that can arise from it due to the small ball layer can re-center the moving piston 301 with sufficient force to resist the remaining rolling friction force due to saturated propane pressure. It is prevented by the presence of the tank.

  Furthermore, in the pure rolling phase, under strong pressure, the oil slowly flows out through the above-mentioned valve located in the first pipe which is not perfectly watertight. This allows the seismic isolation device to return to its initial configuration, allowing the amount of oil in the tank that actually functions as the compensation chamber to be restored.

  Thus, according to the present invention, it can be understood that the combination of the two chambers described above enables the above. When the direct delivery of oil to the second chamber reaches the acceleration of the first detachment, the seismic isolation device always has a coefficient of friction equivalent to the coefficient of the first detachment on the slide base. This is because it is considered that it is always braked by the slide of the bell.

  In contrast, according to the present invention, the combination of the two chambers of the load switching device 100a as described above allows a complete passage of the load Fc from the bell 302 to the omnidirectional bearing 102. Also, in the event of an earthquake having a time interval that exceeds the time interval required for the seismic isolation device to relax, additional cycles, such as those described above, begin to partially release the load Fc to the bell. Caused soon.

  In summary, the load switching device described above allows the conversion of the horizontal relative movement to the downward vertical movement of the thrust means relative to the idle support of the bridge element, which is carried out thanks to the propulsion means, and consequently the load from the idle support. Move to the bearing and perform the friction conversion from slide to rolling.

  For example, FIG. 8 shows an Fx diagram of an automatically operated seismic isolation device according to the present invention, where F is the force transmitted by the seismic isolation device in relative motion in direction X. , X is the relative ground / base movement for the maximum possible deflection.

  Is determined by the curvature radius Rc of the slide base and is proportional to Fc.

  Note that the maximum excursion D-d (where d is the diameter of the bearing) is substantially arbitrary because of the degree of freedom in selecting the size of the diameter D of the rolling base.

  In either case, in the seismic isolation device IA, in order to obtain a height difference between the center and edge of the slide base suitable for preventing drifting resulting from the first detachment impact, D is the curvature. Must match the radius Rc.

  In the event of an earthquake, the force F of the earthquake event rises from zero to the preset first detachment value (Fpd) at the time of the relative movement δ, and is determined by the load switching thereafter. Suddenly drops to the desired value.

  The example of FIG. 9 shows a time diagram illustrating the overall dynamic trend of an automatically operated seismic isolation device according to the present invention.

  When an earthquake event with an acceleration as occurs, the cutting force Ft remains proportional to the acceleration as until the instant t1 when Ft reaches the first desorption value Fpd.

  During the instants t1 and t2, the full load Fc moves to the bearing according to FIG. F1 and stays there for a time period tr, after which the load returns to the idle support and F1 disappears.

  If the relative movement between the ground and the superstructure continues, this process is triggered again after the time period tc.

  The example of FIG. 10 shows a displacement / acceleration diagram in the event of an earthquake, and the relative response of the superstructure with an automatically operated seismic isolation device is shown in the example of FIG. In the example of FIG. 11, for such an earthquake event, the friction coefficient of the slide corresponds to 0.2, and the friction coefficient of the rolling corresponds to 0.003.

  The peak acceleration of the ground is 2.7 g, the amplitude is 40 cm, and the spatial drift is 2 m.

The superstructure receives a peak acceleration corresponding to about 0.3 m / s ² in the first desorption, and the total relative spatial displacement is about 1 cm.

  Instead, the examples of FIGS. 18 and 19 illustrate the structure and function of an externally controlled motion seismic isolation device (ECA) according to the present invention.

  Since the automatic operation mechanism described above is not provided, such a seismic isolation device does not require the above-described casing nor the bridge element to act directly on the drive piston drive. As a result, there is no need for a bracket element combined with a bridge element to automatically operate the propulsion means as previously described for the seismic isolation device IA.

  Thus, the seismic isolation device ECA basically differs from the IA because of the relative load switching device which in this case is much simpler in construction than the automatic operating device described above.

  However, the seismic isolation device ECA retains the overall features of the present invention described above, and they are indicated by the same reference numbers used previously for the seismic isolation device IA.

In particular, in such a case, the load switching device basically comprises:
A bracketless bridge element 103c forming the top of the idle support 101a, indicated by 700 and 701, the first sliding in the appropriate first seat forming the first chamber 304a, the second A pair of moving pistons (thrust means described above) that slide in the corresponding second seat in fluid communication with the second chamber 305a in a hydraulic manner
Propulsion means for supplying a predetermined gas acting on the upper surface of the first moving piston 700 to the switching device Externally controlled on / off means The on / off means advantageously switch An accelerometer that can be generated, and preferably an optical tachymeter, to return to sliding friction when the relative velocity between the ground and the superstructure is stable at the end of the earthquake event. Do.

  The above-mentioned first and second pistons are connected to each other by a connecting element 702 that slides in a receiving seat provided in the piston portion 302a of the idle support 101a inserted into the receiving seat 11 of the bearing 102, and slide movement In one.

  Regarding the propulsion means, the seismic isolation device ECA is preferably provided with a tank 800 containing an appropriate amount of a predetermined saturated gas (preferably, liquid carbon dioxide), and the first pipe 306a is used for the above-described first. To the chamber 304a (when the seismic event is not present, the first moving piston 700 is located at the top).

  An induction solenoid valve 310a that can take substantially the following two positions is provided upstream of the first pipe 306a and between the tank 800 and the first pipe.

  The two positions are an operating position that connects the tank 800 to the first pipe 306a and thus also to the first piston 700, and a non-operating position where the first pipe communicates with a vent 801 that communicates with the external environment. Or the idle position (located upstream of the first chamber in this valve).

  In order to control this solenoid valve, the seismic isolation device ECA according to the present invention further comprises a control unit 802 which controls the solenoid valve in response to a large earthquake signal provided by a dedicated sensor. To allow the carbon dioxide gas in the tank 800 to reach the first chamber 304a described above and push the first piston to apply the switching pressure.

  When there is no earthquake event, the second piston is also integrally connected to the first piston and located at the head of the corresponding seat.

  The slide seat of the second piston is filled with oil and, as already mentioned, has a minimum thickness configuration in view of the absence of pressure on the two pistons when there is no seismic event. The second chamber is in communication and all the loads of the superstructure 500 are located on the idle support 101a.

  Therefore, no load is applied to the bearing 102, and a slide friction state is exhibited as shown in the example of FIG.

  In this case, a “circuit”, which is considered to be strictly hydraulic, is provided by the slide seat and the second chamber of the second piston, while the first chamber and the first pipe are seismically isolated. During operation of the device, the propellant gas mentioned above is present instead of oil.

  When the above sensor (not shown in the figure) detects a seismic wave, the solenoid valve is commanded from the non-operating position to the operating position, the above vent is bypassed, and the tank is connected via the first pipe. In communication with one chamber, carbon dioxide can apply pressure to the first piston.

  The piston pushed downward also moves the second piston via the connecting element described above, and the second piston pushes oil from the slide seat into the second chamber.

  As a result, the piston portion of the idle support is lifted, and the load of this idle support (in section ε) and the superstructure is transferred to the bearing and transferred to rolling friction.

The pressure applied to the oil corresponds to the pressure of carbon dioxide gas multiplied by (first chamber diameter / second chamber diameter) ² .

  When the solenoid valve 310a returns to the non-operating position, carbon dioxide gas is released through the vent 801 to the outside environment. As a result, the first chamber is in a state where there is no pressure in the second chamber, and subsequently, the first and second pistons are raised and returned to the sliding friction position.

  It should be noted that the amount of heat required to obtain the expansion and vaporization of liquid carbon dioxide is low enough to realize that the same tank of carbon dioxide is provided without significant temperature changes.

  Actually, for example, considering that the load Fc = 100 tons is lifted by 0.5 mm, the required switching energy Ec is about 500 J.

Assuming that the situation of −20 ° C. is the worst situation, the required mass of carbon dioxide is due to the thermodynamic table of carbon dioxide resulting in a relative vapor pressure Pv = 2 MPa and a vaporization enthalpy change ΔH = 280 kJ / kg. It is observed that Mco ₂ = Ec / ΔH = 1.75 gr.

The specific entropy change in the conversion is ΔS = 1.2 kJ / Kg ^* K, so the heat required is Q = ΔS (273-20) KMco ₂ = 127cal.

Thus, a steel volume of 150 cm ³ can supply the required heat with a temperature drop below 1 degree Celsius.

  Inserting an aluminum structure with a large wetting surface into the tank is useful for speeding up the process.

  Assuming that the maximum hydraulic pressure is pol = 30 Mpa, the ratio of the diameters of the first and second pistons (or relative slide seats) must be at least in Equation 8 below.

  Here, pol and pv are respectively the maximum pressure required for the oil and the saturated vapor pressure at the lowest temperature conditions brought in place.

  The stroke of the two pistons mentioned above leads to the overall elasticity of the seismic isolation device and is determined by the stroke given by the first piston.

  Advantageously, a pressure reducing device can be added between the tank 800 and the solenoid valve 310a. The pressure reduction device keeps the minimum ambient temperature pressure of the propellant gas entering the solenoid valve to avoid undesirably excessive pressure on the thrust means and end-of-stroke components.

  In summary, the seismic isolation device according to the present invention prevents vertical axis rotation and horizontal tension transmission from the ground to the superstructure during an earthquake, making the effect less than that caused by an artificial earthquake.

  Furthermore, according to a particularly advantageous embodiment of the seismic isolation device according to the invention, the transmission of the remaining two horizontal axis moments is also avoided, so that only the vertical stress at the slide base is transmitted to the superstructure.

  The advantages of the present invention are already apparent in light of the above description, but mainly comprise omnidirectional flow and recirculation of the ball, with respect to the friction between the two objects, between the two objects. The object is to provide a bearing that can guarantee almost complete insulation when a state of relative horizontal movement occurs. This bearing is particularly advantageous for use in friction switching transport assemblies and kinematic seismic isolation devices for moving loads such as heavy loads.

  In particular, in the subject seismic isolation device comprising such a friction switching transport assembly, it is not necessary to use centering and damping elements to eliminate undesirable wind effects.

  Furthermore, the drift velocity on the slide base is very low in the case of the inertial automatic motion type seismic isolation device, and is substantially zero in the case of the control motion seismic isolation device.

  Advantageously, the seismic isolation device of the present invention has a very long resonance period determined by the curvature of the slide base.

  Advantageously, the maximum allowable displacement of the ground is very large and is determined by the size selected for the slide base diameter.

  As an advantage, the acceleration of the first detachment is substantially independent of the adhesion coefficient between the slide base and the idle support, and in fact, in an automatically operated seismic isolation device, the seismic isolation device itself Depends solely on the geometric configuration and the features of the configuration.

  As for the seismic isolation device ECA, it is possible to set an arbitrary operation acceleration depending on the sensor, and it has a wide flexibility in use.

  Furthermore, as an advantage, in the seismic isolation device of the present application, the relative acceleration transmitted to the superstructure is a coefficient of the value of the rolling friction possessed by the bearing on the rolling base at the stage of operation. Reduced. This reduction is obtained for acceleration values having an absolute value greater than that of the first detachment in the case of the seismic isolation device IA, and from the set threshold value in the case of the seismic isolation device ECA. Can be obtained for any acceleration value having a high absolute value.

  Advantageously, the center of thrust of the interaction with the ground of a system comprising a plurality of seismic isolation devices according to the invention is always at the vertical line of the superstructure's center of gravity, so that the superstructure is extremely It is stable.

  Advantageously, translational and rotational insulation of the vertical axis of the superstructure is ensured while there are no kinematic discrepancies as described above.

  Advantageously, problems with cold welding are eliminated due to the fact that rolling layer balls support the weight of the superstructure only during an earthquake.

  Furthermore, accurate and easy centering after an earthquake event can be obtained.

  Furthermore, the seismic isolation device according to the present invention can be manufactured without using much of the heavy material (steel) mass used to manufacture the slide surface, and therefore the manufacturing cost is low, compared with known seismic isolation devices. Easier to install and maintain.

  Various modifications may be made to the ball bearing, friction switching transport assembly, and seismic isolation device according to the illustrated and described embodiments to meet the specific needs needed by those skilled in the art, All within the scope of protection of the present invention as defined by the appended claims.

Claims (29)

A slide plate having a substantially circular bottom surface intended to roll on a ball layer comprising a plurality of balls;
A boundary element for the ball layer having a substantially ring shape surrounding the bottom surface and having an inner knife-like edge;
A roller bearing comprising: a frustoconical ring-shaped gap space for receiving and recirculating a ball that is open toward the bottom surface.   2. The apparatus according to claim 1, further comprising a predetermined number of passages for inserting a predetermined number of balls into the gap space at a position substantially opposite the bottom surface. bearing.   The bearing according to claim 1, wherein the slide plate has a substantially frustoconical inclined side surface.   The bearing according to claim 3, further comprising a cover cap that is combined with the slide plate and disposed in a predetermined distance from the side surface so as to define the gap space.   The bearing according to claim 4, wherein the boundary element is constrained in a rotational direction with respect to the cap and movable in an axial direction with respect to the cap.   A storage seat for engaging the bearing with a predetermined object is further provided, and the storage seat is provided on the slide plate at an end opposite to the bottom surface. The bearing according to any one of 5.   The bearing according to any one of claims 3 to 6, wherein a chamfered edge is defined between the side surface and the bottom surface.   The bearing according to claim 1, wherein the gap space has an end portion defined by an annular groove.   The bearing according to claim 1, wherein the bottom surface is a flat surface or a spherical cap shape. A conveying assembly for controlled switching from sliding friction to rolling friction and rolling friction to sliding friction,
An idle support configured to support a predetermined load Fc and having a high adhesion coefficient;
A rolling element housed inside the idle support and slidable substantially freely vertically within the idle support over a predetermined limited length section;
A switching device configured to transfer the load from the idle support to the rolling element, and further from the rolling element to the idle support;
A transport assembly comprising: The switching device is
Thrust means capable of acting on the rolling element;
A force F1 substantially corresponding to the load Fc, configured to generate a force F1 acting on the thrust means over a predetermined time period during which the load is transferred from the idle support to the rolling element. Propulsion means,
Activating means for controlling the propulsion means;
11. A transport assembly according to claim 10 comprising:   12. A transport assembly according to claim 11, wherein the thrust means is a mechanical means acting on the rolling element.   12. A transport assembly according to claim 11, wherein the thrust means is a hydraulic means acting on the rolling element. The rolling element comprises a roller bearing;
The roller bearing is
A slide plate having a substantially circular bottom surface resting on a ball layer composed of a plurality of balls;
A boundary element for the ball layer having a substantially ring shape surrounding the bottom surface and having an inner knife-like edge;
14. A transport assembly according to claims 10-13, comprising a frustoconical ring-shaped gap space for receiving and recirculating balls open towards the bottom surface. A seismic isolation device for isolating the superstructure from the movement of the ground on which the superstructure is located in the event of an earthquake,
A slide base integral with the ground,
An idle support having a high coefficient of friction, arranged above the slide base and configured to support a predetermined load Fc depending on the superstructure;
A slide plate having a substantially circular bottom surface resting on a ball layer composed of a plurality of balls disposed on the slide base, and a substantially ring-shaped inner knife surrounding the bottom surface; Roller bearing comprising a boundary element for the ball layer having a conical edge and a frusto-conical ring-shaped gap space for receiving and recirculating the balls open towards the bottom surface When,
A switching device configured to transfer the load from the idle support to the roller bearing, and further from the roller bearing to the idle support;
A seismic isolation device.   The seismic isolation device according to claim 15, further comprising a fixed header integral with the upper structure.   The seismic isolation device according to claim 15 or 16, wherein the slide base has a flat or spherical concave cap shape.   The seismic isolation device according to any one of claims 15 to 17, further comprising a sheet of a predetermined metal or metal alloy that is integral with the slide base and covers the slide base.   The seismic isolation device according to any one of claims 16 to 18, further comprising a bridge element connected directly below the fixed header via a ball joint. The switching device is
Thrust means acted on the roller bearing;
A force F1 substantially corresponding to the load Fc, the force F1 acting on the thrust means over a predetermined period of time when the load is transferred from the idle support to the roller bearing. Propulsion means,
The seismic isolation device according to claim 15, comprising:   The switching device is provided with an activating means for controlling the propulsion means, and when the predetermined horizontal acceleration value of the ground is reached, the propulsion means can be operated by inertia due to the movement of the ground. The seismic isolation device according to any one of claims 15 to 20.   22. The seismic isolation device according to claim 20 or 21, wherein the thrust means comprises a first chamber and a second chamber that are inflatable under hydraulic pressure and are in fluid communication with each other.   23. The first inflatable chamber is defined within the idle support, and the inflatable second chamber is configured between the idle support and the roller bearing. Seismic isolation device.   The seismic isolation device according to claim 23, wherein the increase in the hydraulic pressure in the first chamber occurs earlier than the increase in the hydraulic pressure in the second chamber.   The seismic isolation device according to any one of claims 15 to 21, wherein the switching device includes on / off means for controlling the propulsion means with autonomous energy.   26. The seismic isolation device according to claim 25, wherein the on / off means comprises a field and / or remote sensor.   27. The seismic isolation device according to claim 25 or 26, wherein the thrust means is operated by thrust of a predetermined gas or gas mixture supplied by the propulsion means.   The seismic isolation device according to any one of claims 25 to 27, wherein the predetermined gas is carbon dioxide.   29. The seismic isolation device according to claim 28, wherein the carbon dioxide is a liquid.

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