Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/02—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum
  • F16F9/0209—Telescopic
  • F16F9/0218—Mono-tubular units
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
  • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
  • F16F9/32—Details
  • F16F9/34—Special valve constructions; Shape or construction of throttling passages
  • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
  • F16F9/3485—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of supporting elements intended to guide or limit the movement of the annular discs

Definitions

• the invention relates to an air spring, consisting of a hollow working cylinder, which is closed with a first bottom oriented towards the one suspended subject, on one side, and with a second bottom with a hole, on the other side, in which sealed piston rod are fitted, the end of the piston hole protruding from the working cylinder is adapted to allow fixing to the other suspended subject and the other end of the rod, protruding into the working cylinder, is provided with a sliding piston fitted in the working cylinder, whereas the piston having axial holes, with a sliding throttle element fitted axially opposite the holes to control the working medium flow through the axial holes .
• Patent document- US 2006/0231358 describes impact absorber featuring working cylinder fitted with a lug to car body and piston with a piston ring, having a lug at its free end for connection with car wheel suspension.
• the piston has two sets of axial holes, .arranged symmetrically with the piston rod axis to allow' working medium to flow from the space above the piston to the space below the piston and vice versa.
• Valve discs adjoining to piston front walls are provided at both frontal piston sides,' opposite the holes. Both the piston and valve discs from both sides of the piston are fitted in sequence at the free end of the piston rod.
• Valve discs are axially fixed with space rings and nuts, screwed at the piston rod. By tightening the nut, valve disc tension will be increased and, thus, working medium flow will be throttled. However, disc tension can be adjusted only after removal of the discs from the working cylinder, hence, setting the disc position and impact absorber rigidity cannot be changed, when the piston has been installed in the working cylinder.
• Patent document WO 94/19619 describes impact absorber consisting of a working cylinder with a piston and piston ring. Both the piston and -.the piston ring have inner bore with a rotation-fit control tube and rotation-fit control rod fitted in the tube. The control rod and control tube, protruding outside the free end of the piston rod axially, are fitted with elements intended for turning.
• the piston has axial holes allowing the medium to flow from the space above the piston to the space below the piston and vice versa.
• Axial moving impact absorption discs with axial holes, installed in the same axis as the piston in circle, are provided on the side of the piston reverse to the piston rod, opposite axial holes.
• Two absorber valves adjoining alternatively to one of opposite front surfaces of the discs, are fitted between absorber discs.
• one disc valve When working medium flows in one direction, one disc valve will close, flow through axial holes of one absorber disc and the other valve will be pushed away from the second absorber disc, thus allowing medium to flow through the holes.
• One control disc is fitted on the control tube end and the second contro'l disc is joined with the control rod end.
• Control discs can be turned, thus adjusting impact absorber rigidity, using control elements of the rod, without disassembling the impact absorber.
• the unit as described in WO 94/19619. is rather sophisticated and difficult to manufacture.
• the control tube and control rod are fitted in the hollow space of the piston rod, hence, this design cannot be used for double-action .impact absorbers, in which the cylinders are installed in one axis, one cylinder in the other.
• the aim of the invention is to eliminate the drawbacks of the current designs and to develop a spring featuring simple design, particularly, double-action impact absorbing spring, with absorbing characteristics, adjustable in site (no need of dismantling) .
• the aim of the invention is to provide a spring featuring simple de'sign, allowing impact absorbing characteristics be adjusted also during operation of the spring.
• the aim of the invention is to provide a spring, able to absorb impact energy generated by compression and liberate accumulated energy - at once or subsequently, in a controlled manner.
• the aim of the invention is to provide a spring of the family as described before, featuring high reliability, simple design, being easy to disassemble and assemble, which can be produced in a wide range of dimensions.
• the aim of the invention is to provide an air spring with a piston having axial holes allowing working medium to flow through the holes and having a throttle ring opposite axial holes of the piston>at piston rod's side to throttle working medium flow through the axial holes, the spring slightly resisting to slow pushing inside the piston rod and highly resisting to fa'st ⁇ pushing inside the piston rod.
• the aim of the invention is to provide an air spring as described above, allowing adjustment/control of the resistance to fast inserting.
• the aim of the invention is to have an air spring of the .family as described above that would efficiently comply with the requirements, have a simple design, installation, assembly, maintenance and extreme durability. Summary of the invention
• a compressive air spring comprising a hollow working cylinder, closed on one side with a first bottom oriented to the one suspended element and on the other side closed with a second bottom with a hole to a sealed piston rod, its end protruding from the working cylinder is adapted for attachment to the other suspended object and its end protruding into the working cylinder is provided with a sliding piston fitted in the working cylinder, whereas the piston is provided with axial holes, opposite which a throttling sliding element supported axially to control working medium flow through the axial holes, according to the invention, the principle of which consists in that the throttling element is formed by a flat throttling ring arranged co-axially on the outer side of the piston rod between the piston and the end of an outer axially-movable defining tube, fitted co-axially outwardly on the piston rod and going through the hole in the second bottom, whereas an element defining stop position
• the element defining stop position of the throttle ring can be advantageously formed by 'an outer shoulder made up at one end of an axially-movable inner defining tube fitted between the piston rod and the outer defining tube, going through the hole of the throttle ring, whereas the other end of the inner defining tube going through the hole in the second bottom.
• the element defining stop position of the throttle ring can be advantageously provided by springs or a ring, fitted between the piston (2) and the throttle ring.
• the inner defining tube can be advantageously provided with an inner thread for running thread fit on the piston rod and with an outer thread for running thread fit of the outer defining tube, whereas the free ends of both the outer defining tube and the inner defining tube protruding from the working cylinder are provided with elements to set angle positions in relation to the piston rod.
• the piston rod can be advantageously provided with axial bore for sliding fit on one end of a guide cylinder, the other end of which being connected to the first bottom, whereas the piston of annular form being fitted between the guide cylinder and the outer working cylinder.
• the outer working cylinder with an outer annular piston and an outer piston rod provided .with axial bore for sliding fit on the working cylinder and for movement of the outer piston between the first bottom and the second bottom of the outer working cylinder can be advantageously fitted coaxially, outside the working cylinder, the piston rod and the outer piston rod being oriented in opposite directions and the first bottom of the outer working cylinder and the second bottom of the inner working cylinder being created of one piece.
• the end of the outer piston rod can be advantageously fitted on the first bottom of the working cylinder and the end of the piston rod fitted piston of the accumulation unit, whereas the space between the piston and the second bottom of the working cylinder being connected by a tube with the space between the piston and the first bottom, across a drive of an alternator or across a pump connected to an electromotor.
• An additional throttle ring for axially-sliding movement in the working cylinder can be advantageously fitted opposite to the axial holes on the side of the -piston opposite to the piston rod, whereas a spring and a stop element, going through the axial hole being provided between the throttle ring and the additional throttle ring 'to set maximum distance between both rings.
• a contact element to define maximum distance between the throttle ring and the' additional throttle ring can be advantageously formed by a contact pin, one end of which being fixed to one of the throttle ring and additional throttle ring (60) assembly, and the second end of which, passing through the other one of the throttle ring and additional throttle ring assembly is terminated by an outer shoulder.
• the piston opposite to the piston rod can be advantageously provided with an axial stop of the throttling ring, formed by the end of the piston rod passing through the threaded hole of the piston, whereas the threaded hole and the end of the piston rod are provided by running threads in the area of contact.
• the working cylinder an be advantageously provided with a radial guide pin, protruding into a guide groove of an outer slotted piece firmly attached to the inner defining tube, and with a guide pin protruding into a guide groove of an inner slotted piece, attached to the outer defining tube.
• the working cylinder can be advantageously pass through the sealed hole of the second bottom of an additional working cylinder, which opposite first bottom is adjusted for fitting to the first suspended element. Volume of the working cylinder can be advantageously filled with pressurized medium exceeding atmospheric pressure.
• the outer defining tube on the piston rod or on the inner defining tube and the inner defining tube on the piston rod can have axially-moving fit, e.g. axial grooves, which' " ends can be interrupted to allow fixing of position of the' outer defining tube or the inner defining tube.
• the outer defining tube can have rotation fit on the piston rod or on the inner defining tube and have axially shaped collar on its end to engage with axial collar of the throttle ring, on near side to the outer defining tube, the throttle ring being fitted in the axial groove, provided on the piston rod or on the inner defining tube.
• the end of the inner defining tube may have cutouts or polygonal shape, the throttle ring being fitted axially, with no rotation, however, on the inner defining tube.
• the throttle ring can have circular, oval or otherwise shaped holes, which - depending on turning position of the throttle ring - will overlap axial holes in the piston, thus adjusting the quantity of working medium flowing through the axial holes in the piston.
• the advantage of the air spring as described herein is, particularly, ability of its characteristics to be adjusted easily and using simple elements and also changed during operation of the spring.
• the air spring as described herein can be used in double-action design in variety of industrial applications.
• the air spring as described herein allows accumulation of energy generated by compression of working medium, namely gas, in the working cylinder of the unit and easy liberation of this energy at once or in an interrupted or subsequent way, by way of controlled putting the throttle ring away from the axial holes in the piston, thus allowing the working medium to flow through the axial holes in the piston.
• the air spring as described herein consists of simple, standard-design components that are easy-to manufacture, hence, it has a simple technical design and is easy to fit and remove.
• the air spring as described herein is highly reliable in operation, owing to standard components that have proved their quality in use in the field of shock-absorbers.
• the air spring as described herein can be manufactured and operated in a large variety of dimension, from working cylinder diameter of several centimeters up- to over one meter.
• the air spring as described herein is not subject to spring-fatigue, the shock- absorbing elements of the unit, virtually, are not subject to wear and tear, compression of the spring can be largely- adjusted by way of changing initial pressure in working cylinders.
• the shock-absorbing air spring as described herein can be compressed up to 40 per cent of its initial length.
• the air spring as described herein is light in weight, can be made of light aluminium alloys, with unrivalled low production costs compared with conventional air springs and coil springs made of steel.
• the advantage of the air spring as described herein is mainly its low resistance against pushing the piston rod slowly and high resistance against pushing the piston rod quickly.
• the advantage of the unit as described herein allows easy adjustment of resistance both in case of slow and quick pushing the piston rod and to make this adjustment from outside and, - where required - in operation, while maintaining the advantage of being able to adjust the resistance against pushing out from exterior environment and - where required - also in operation.
• the invention allows adjusting spring resistance against pushing out and slow and quick pushing in depending on piston rod travel, i.e. on the level of spring compression.
• Another advantage of the air spring as described herein is its ability of being used in combination with another air sprig. Last but not least, the advantage of the air spring as described herein is high efficiency, possibility of various adjustments of the unit during operation, simple technical design, easy assembly, maintenance and long service life.
• the air spring as described herein can fully replace any conventional steel spring, particularly in the automotive and aircraft industry.
• Drawing No.l shows longitudinal section of the spring (simple design); Drawing No.2 shows longitudinal section of spring coils; Drawing No.3 shows various positions of the throttle ring; Drawing No.4 shows longitudinal section of air spring parts, with springs fitted between the piston and the throttle ring; Drawing No.5 shows longitudinal section of spring components with .a thrust ring fitted between the piston and throttle ring; Drawing No.6 shows longitudinal section of double-action air spring; Drawing No.7 shows longitudinal section of the recoil damper; Drawing No.8 shows longitudinal section of the energy accumulation unit; Drawing No.9a shows longitudinal section of the air spring as specified herein at elongation; Drawing No.9b shows longitudinal section of the air spring as specified herein at slow compression; Drawing- ' No.9c shows longitudinal section of the air spring as specified herein at quick compression; Drawing No.10 shows longitudinal section of the air spring as specified herein; Drawing No.11 shows guide links of the spring as specified herein; and Drawing No.12 shows other proposed design options of the
• the air spring as shown in Fig. No. 1 in an exemplary way, consists of a hollow working cylinder 1 with piston 2, fitted for sliding in the working cylinder 1, between the first bottom 4 and the second bottom 5.
• the piston 2 is linked with the piston rod 3, moving -in the hole 6 made in the second bottom 5.
• the piston 2 has axial holes 8.
• the axial, sliding and rotating inner defining tube 12 is fitted on the piston rod 3, and the outer defining tube 11 is fitted on the inner defining tube 12, both the inner defining tube 12 and the outer defining tube 11 going through the hole 6 made in the second bottom 5.
• the piston 2 has a circumferential sealing element 2a for separation of the space in the working cylinder 1 above the piston 2 and below.
• the piston rod 3 has a circumferential sealing element 3a for sealing space in the working cylinder 1 aga'inst the outer environment, the inner defining tube 12 has circumferential sealing 12a and the other bottom 5 has sealing 5a in the hole 6. Sealing 3a is fitted between the piston rod 3 and the inner defining tube 12, sealing 12a is fitted between the inner defining tube 12 and the outer defining tube 11, sealing 5a is fitted between the tube 11 and the second bottom 5.
• the axially-moving flat throttle ring 7 is fitted between the end of the outer defining tube 11 and piston 2 to throttle spring medium flow.
• the inner defining tube 12 has circumferential collar 13 at its end adjacent to the piston 2; outer diameter of the collar is bigger than inner diameter of the throttle ring 7.
• Recess 9 has been provided in the piston 2, against circumferential collar 13 of the defining tube 12, thus allowing circumferential collar 13 to fit fully into one of dead centres of the piston 2.
• the piston rod 3, the inner defining tube 12 and the outer defining tube 11 go through the hole 6 made in the second bottom ,5, with the outer defining tube 11 being sealed against the ⁇ hole 6.
• the front radial ring 20 is fitted on the end of the " 'piston rod 3 protruding from the working cylinder 1.
• the piston rod 3 has outer (male) thread 17 for transmission of rotation into axial movement along its length or, advantageously, at the front radial ring 20, between the front radial ring 20 and the second bottom 5 of the working cylinder 1.
• the end of the inner defining tube 12, protruding from the working cylinder 1, is fixed to the radial ring 19 and has inner (female) thread 14 for fit on outer thread 17 on the piston rod 3.
• the connection between outer thread 17 on the piston rod 3 and inner thread 14 on the inner defining tube 12 transmits rotation of the radial ring 19 into axial movement of the inner defining tube 12 against the piston rod 3.
• circumferential collar- 13 on the other end of the inner defining tube 12 will be-pushed out/into recess 9 in the piston 2.
• the end of the -outer defining tube 11, protruding from the working cylinder' 1, is joined with and fixed to the radial ring 16 and has inner thread 16 to engage with outer thread 15 of the inner defining tube 12.
• the moveable threaded connection of inner thread 16 on the outer defining tube 11 and outer thread 15 of the inner defining tube 12 transmits rotation of the radial ring 18 to axial movement of the outer defining tube 11 in relation to the inner defining tube 12.
• the distance between the throttle ring 7 and front surface of the piston 2 determines the magnitude of throttling medium flow through the holes 8 in the piston 2.
• radial rings 18, 19, 20 specified above, other generally-applicable systems can be utilized for changing of rotation movement of radial rings 18, 19, 20 to axial movement of the outer defining tube 11, inner defining tube 12 and piston rod 3.”
• the outer defining tube 11 can be fitted on the piston rod 3 or on the inner defining rod 12, and the inner defining rod 12 on the piston rod 2 can be fitted in axially-moving fit, e.g. in axial groove's that may be cut at their ends to fix the position of the 'outer defining tube 11 or the inner defining tube 12.
• the conventional elements fitted on the free end of the piston rod 3, protruding from the working cylinder 1, can be used for adjustment of axial position of the inner defining tube 12 and the' v -outer defining tube 11.
• the outer defining tube 11 can rotate on the piston rod 3 or on the inner defining tube 12, having circumferential shape on its end to engage with axially-shaped front surface of the throttle ring 7, towards " the outer defining tube 11; the throttle ring 7 must be fitted in axially-shaped groove on the piston rod 3.
• the end of the inner defining tube 12, towards the piston 2 can be fitted with cutouts or polygonal shape, the throttle ring 7 being fitted to the inner defining tube 12 in axial and moving fit, however, no rotation.
• the throttle ring 7 can have circular, oval or otherwise shaped holes that - depending on turning angle of the throttle ring 7 - will overlap axial holes in the piston 2, thus controlling throttle intensity of medium flow through axial holes 8 in the piston 2.
• the air spring as shown in Fig. 1 shall be utilized for power transmission, absorption a ' nd damping of impacts between the radial ring 20 on the piston rod 3 and the first bottom 4 of the working cylinder 1.
• the working cylinder 1 is filled with compressed working medium; e.g. air, inert gas.
• working medium is distributed in the entire space between the piston 2 and the first bottom 4 of the working cylinder 1.
• working medium pressure can be increased at the initial dead centre of the piston 2 or reduced, as the case may be, in the conventional way.
• the piston 3 with the inner defining tube 12 and outer defining tube 11 will enter into the working cylinder 1, thus reducing cylinder volume and increasing working medium pressure in the working cylinder 1.
• the working medium While the piston 2 moving away from the second bottom 5 towards the first bottom 4, the working medium will be compressed due to reduction of cylinder volume and, at the same time, working medium will come from the space between the piston 2 and the first bottom 4 through axial holes 8 into space between the piston 2 and the second bottom 5.
• the throttle ring 7 While the piston 2 is moving away from the second bottom 5 towards the first bottom 4, the throttle ring 7 will be in contact with the end of the outer defining tube 11.
• the distance between the throttle ring 7 and axial holes 8 can be modified by adjustment of axial position of the outer defining tube 11, thus throttling medium flow from space above the piston 2 into space below the piston 2. While the piston 2 is moving from the first bottom 4 towards the second bottom 5, the throttle ring 7 will, fit tightly to the front side of the piston 2 and close the holes 8. While the inner defining tube 12 moves away from the piston 2, circumferential collar 13 becomes engaged with the throttle ring 7, moving the throttle ring 7 away from the holes' 8, thus allowing working medium to flow from space below the piston 2 to space above.
• the magnitude of throttling medium flow will be modified by changing the distance between the throttle ring 7 and axial holes 8.
• FIG. 2 shows threads on the ends of the piston rod 3, inner defining tube 12 and outer defining tube 11.
• Fig. 2 indicates outer thread 17 on the piston rod 3 engaging with inner thread 14 on the inner defining "tube 12 and outer thread 15 of the inner defining tube 12 engaging with inner thread 16 of the outer defining tube 11.
• Fig. 3 illustrates possible adjustments of the throttle ring 7 in relation to the axial holes 8 in the piston 2.
• position A the end of the outer defining tube 11 is at certain distance from the piston '2, thus providing for sufficient clearance of the throttle ring 7 to come away from the piston 2, while the piston 2 will be pushed in direction b, thus allowing fully working medium to flow through the axial holes 8.
• circumferential collar 13 will fit fully into recess 9 at the front side of the piston 2 up to the stop.
• the piston 2 having'been released, the throttle ring 7 will fit closely to the piston 2 and fully close working medium flow through the axial holes 8.
• the piston 2 will be pushed in direction b with a damping characteristic proportional to the throttling magnitude of medium flow by the ring 7.
• circumferential collar 13 In position D, circumferential collar 13 is slightly lifted from recess 9 in the face of the piston 2 and the end of the outer defining tube 11 is closer to the axial holes 8 as compared to positions A and B.
• the space for movement of the throttle ring 7 is defined in such a way that the piston 2 moves with considerable damping when being pushed in/out in direction b.
• the position of the inner * defining tube 12 with circumferential collar 13 as well as the position of the outer defining tube 11 can be continually adjusted and, hence, the damping force of the working spring during movement of the piston 2 in both directions can be continuously adjusted.
• the damping force of the air . spring as specified herein can be adjusted between one limit setting in which the damping force during movement of the piston 2 in both directions is low, and the other limit setting in which the damping force is low at pushing-in of the piston 2, and pushing-out of the piston 2 is fully disabled.
• the speed " - at which the piston 2 will be pushed out of the working cylinder can be adjusted by positioning circumferential collar 13.
• the inner defining tube 11 having been fully screwed inside, the throttle ring will be pushed towards the axial holes 8> thus preventing the piston 2 from any movement.
• unscrew the outer defining tube 11 thus pushing its end away from the axial holes 8 and opening medium flow through the axial holes 8.
• the piston will move slowly, proportionally to the distance between the throttle ring 7 and the axial holes 8.
• the speed of pushing the piston 2 into the working cylinder will be adjusted by positioning of the outer defining tube 11 with circumferential collar 13.
• the device to define the distance between the throttle ring 7 and the piston 2 is made up by coil springs 82.
• One end of the springs fits into recess 81 in the axial holes 8 in the piston 2 and the other end on the throttle ring 7.
• the throttle ring 7 can be moved against resistance of the coil springs 82, thus adjusting the distance between the throttle ring 7 and axial holes 8.
• the recess in the axial holes' 8 can be made at the front side of piston 2, one end of coil springs being fitted in this recess, with distance bars (not shown on the figure) fitted between the other - free - ends of * the coil springs and the throttle ring 3.
• the throttle ring 3 Moving towards the piston 2, the throttle ring 3 will apply pressure onto distance bars, pushing them into the axial holes 8, while coil springs 82 will extend. When extended, the coil springs 82 will push" on the throttle ring, thus forcing it away from the piston.
• the 'device to set the distance between the throttle ring 7 and the piston 2 consists of the thrust ring 91 arranged in the same axis around the piston rod 3 between the end of the outer defining tube 11 a piston 2.
• the thrust ring 91 can be made up ih ' single-unit wit the piston 2.
• the throttle ring 7 is fittedf.between the end of the outer defining tube 11 and the ⁇ 'front surface of the thrust ring 91. Clearance of this ring allows it to come near to the axial holes 8 and to throttle medium flow through the holes, while the piston 2 moves towards the second bottom 5 (not shown) with the piston rod 3 and 'the outer defining tube 11.
• a double-action design of the air spring specified herein is shown in Fig.
• the inner working cylinder 1, piston rod 3 and piston 2, the inner defining tube 12 and outer defining tube 11 are fit in the same way as shown in Fig. 1.
• the outer working cylinder 101 with the outer piston 102 of annular section and the outer piston rod 103 with axial bore 103c, intended for sliding fit on the working cylinder 1 and movement of the outer piston 102 between the first bottom 104 and the second bottom- 105 of the outer working cylinder 101 are arranged coaxially outside the working cylinder 1, the piston rod 3 and the outer piston rod 103, being in direction away from the pistons 2, 102 and oriented in opposite directions, and the first bottom 104 of the outer working cylinder 101 and the second bottom 5 of the working cylinder 1 are made as a single unit.
• the outer defining tube 111 going through the hole 106 in the second bottom 105 is fitted on the hollow outer piston rod 103 (axial, sliding and rotation fit) , and the throttle ring 107 is fitted between the end of the outer defining ⁇ tube 111 and the outer piston 102.
• the inner defining tube 112 going through the hole 106, made in the second bottom 105 and having circumferential collar 113 on the outer piston 102, > is fitted (axial and sliding fit) between the outer piston rod 103 and the outer defining tube 111, the throttle ring 107 being fitted in the inner defining tube 112, between the end of the outer defining tube 111 and circumferential collar 113 of the inner defining tube 112.
• the piston 102 has circumferential sealing 102a to seal the space in the working cylinder 101, above and below the piston 1022.
• the piston rod 103 has a sealing element 103a on its circumference
• the inner defining tube 112 has a sealing element 112a on its circumference
• the second bottom 105 has a sealing element 105a in the hole 106.
• the sealing element 103a is intended for sealing the piston rod 103 from the inner defining tube 112
• the sealing element 112a is intended for sealing the inner defining tube 112 from the outer defining tube 111
• the sealing element 105a is intended for sealing the outer defining tube 111 from the second bottom 105.
• the inner defining tube 112, the outer defining tube 111 and the outer piston rod 103 have working threads, as shown in Fig.” 2: the inner defining tube 112 has the inner thread 114 for moving fit on the outer thread 117 of the outer piston rod 103, and the outer thread 115 for moving fit in the inner thread 116 of the outer defining tube 111. In the extreme position of the inner defining tube 112, circumferential collar 113 protrudes into the outer piston 102.
• the outer defining tube 111 and/or the inner defining tube 112 have radial rings 118 and/or 119 for adjustment of angular position of both elements on their free ends protruding from the worki ' hg cylinder 101.
• the radial ring 118 of the outer defining tube 111 makes a bottom of the cylindrical handle 118c, which cylindrical walls fit, with certain clearance, with the outer surface of the outer working cylinder 101, and the radial ring 18 of the outer defining tube 11 makes a bottom of the cylindrical handle 18c, which cylindrical walls fit, with certain clearance, with outer circumference of the first bottom 104 of the outer working cylinder 101.
• the thrust ring 120 is connected with the circular plate 122, having a centre hole 121 allowing free flow of air or medium into the hollow space in the outer piston rod 103.
• Fig. 2 indicates the thread 117 of the piston rod 113, engaging with the inner thread 114 of the inner defining tube 112 and the outer thread 115 of the inner defining tube 112, engaging with the inner thread 116 of the outer defining tube 111.
• the air spring as shown in Fig. 6 is intended for transmission of force and absorption of impacts between the thrust ring 20 of the piston rod 3 and th " e thrust radial ring 120 of the piston rod 103 fitted with a plate 122.
• the air spring--as specified herein has two separate pressure chambers, made up by working cylinders 1, 101. As the spring is being depressed, the pistons 2, 102 enter into the chambers above, in opposite directions. As the air spring is being depressed, throttle rings 7, 107 reduce working medium flow through the holes 8, 108 and slow down movement of the pistons 2, 102.
• the throttling magnitude can be controlled by adjusting position of the outer defining tubes 11, 111 in relation to the pistons 2, 102.
• the distance between the throttle rings 7, 107 and the holes 8, 108 can be controlled by"' axial movement of the inner defining tubes 12, 112, using circumferential collars 13, 113.
• the throttling magnitude, and " thus the speed of movement of the pistons 2, 102 away from one another will depend on the distance between the throttle rings 7, 107 and the holes 8, 108.
• Pressure in the working cylinders 1, 101 can be adjusted in such a way that pressure in the cylinder 101 will be higher than that in the cylinder 1, consequently, only the cylinder 1 will be in operation at Tow load.
• the working cylinder 101 will start working at certain load, e.g. 80% of that of the working cylinder 1.
• the air spring as shown in Fig.7 can be used for absorption of recoil energy of gun shot.
• the gun barrel 30 is fitted in the guide cylinder 32, making _the inner cylindrical wall of the working cylinder 101 of the air spring, which basic design is otherwise identical to that shown in Fig. 6.
• the first bottom 104 of the working cylinder 101 is fitted on the gun carriage stand 33 (not shown) .
• the annularly-shaped piston 102, joined with the piston rod 103 going through the hole 106 in the second bottom 5, is fitted in the space between the first bottom 104 and the second bottom 105.
• the piston rod 103 has a bore intended for fit on the outer surface of the guide cylinder 32, sealed using 'the element 103a.
• the other components and parts of the air spring unit are identical to the outer air spring as shown in Fig. 6.
• the axially-sliding and rotating inner defining tube 112 with circumferential collar 113, reaching into recess 109 provided in the piston 2, is fitted on the piston r'od 103.
• the axially-sliding and rotating outer defining tube 111 is fitted on the inner defining tube 112.
• the axially-moving throttle ring 107 intended for controlled closing of the axial holes 108 or controlling the flow through the holes, is fitted between the end of the tube 111 and the piston 2.
• the piston rod 103, inner defining tube 112 and outer defining tube 111, at the ends protruding from the working cylinder 101, have radial rings 120, 118, 119 with cylindrical handles 118c, 119c to turn the inner defining tube 112 and outer defining tube 111 in relation to the piston rod 103 using threads.
• the air spring as shown in Fig. 7 is fixed to the gun stand with its first bottom 104.
• the gun barrel 30 goes through the guide cylinde'r 32 and its shoulder 31 stems against the radial front.'ring 120. At shooting, the gun barrel is subject to backward force, transmitted to the radial front ring 120 of the position rod 103 across the shoulder 31, and the piston 102 will be forced towards the first bottom 104.
• Movement of the piston 102 towards the first bottom 104 will be absorbed by means of reduction of spring medium flow through the axial holes 108.
• the throttling magnitude depends on the distance between the axial holes 108 that can be adjusted by axial sliding of the outer defining tube 111, like in the preceding design versions. Return of the piston 102 and gun barrel 30 into their ⁇ initial position will be damped by throttling the spring medium flow through the axial holes 108 in the opposite direction...than that at recoil of the gun barrel 30 at the shot. Throttling magnitude of medium flow at return of the piston 102 in the initial position depends on the distance between the throttle ring 107 and the axial holes 108.
• the distance can be adjusted by axial movement of circumferential collar 11'3 on the inner defining tube 112.
• the inner defining tube with circumferential collar 113 will be moved away from the piston 102, thus allowing the piston 102 to move and expand the spring.
• Absorption of energy of the gun barrel 30 can be adjusted for both directions separately and independently.
• the air spring is intended for power accumulation devices.
• the electric energy can be transferred into energy of pressurized air, and during periods of time with high power tariff, energy, of pressurized air will be transferred back to power".
• the power accumulation system as shown in Fig. 8 consists- t>f a hydraulic accumulator loaded with pressurized air.
• Th"e v air spring is arranged between the piston 40 and the first bottom 41 of the working cylinder 43 of the accumulation system 44.
• Radial groove 51 connecting the inner space of the hollow outer piston rod 103 with a hole in the first bottom 41 for entry of the connection line 45 into the space between the piston 40 and the first bottom 41, is provided in the first 5 bottom 41 of the working cylinder 43.
• the space between the piston 40 and the second bottom 42 of the working cylinder 43 is connected by the tube 45 with the space between the piston 40 and the first bottom 41 via a drive unit 46 of the alternator 47 or via a pump 48 with r electric engine 49.
• Space is provided between the piston 40 with sealing 40a and the second bottom 42 that is connected with the space between the piston 40 and the first bottom 41 by the tube 45, via a drive unit 46 of the power generator 47 or via a pump 48 connected with the electromotor 49.
• the electromotor 49 works and the pump 48 is pumping fluid from the space between the piston 40 and the first bottom 41 into the space between the piston 40 and the second bottom 42.
• the piston 2 By pressure of the fluid pumped into the space between the piston 40 and the second bottom 42, the piston 2 will be forced into the working cylinder 1, inner volume of the working cylinder 1 decreases and gas pressure in the working cylinder 1 increases.
• the piston 102 will be forced into the outer working cylinder 101, its volume decreases and gas pressure in the outer working cylinder 101 increases.
• the pistons 2, 102 After stopping fluid into the space between the piston 40 and the second bottom 42 of the accumulator 44, the pistons 2, 102 will stop moving and, and when the pistons ⁇ 2, 102 move backwards, the throttle rings 7, 107 will fit tightly to the axial holes in the pistons 2, 102, thus causing the pistons 2, 102 to stop.
• the inner defining tubes 12, 112 will be moved axially, turning the radial rings 118, 119, 120 and 18, 19','- 20, and circumferential collars 13, 113 will be moved away from the pistons, and the throttle rings 7, 107 will open the axial holes 8, 108 in the pistons 2, 102, gas starts flowing through the axial holes 8, 108 and springs start expanding by pressure in the working cylinders 1, 101.
• Forced flow of fluid from the space between the piston 40 and the second bottom.42 back into the space between the piston 40 and the first bottom 41 will set the drive unit 46 of the generator 47 in movement and the generator will supply- power back to the mains .
• the air spring in Fig. 9a, 9b, 9c is shown schematically in three working positions.
• the first position in Fig. Ia shows forcing the piston rod 3 from the working cylinder 1
• the second position (Fig. 9b) ' shows the piston rod 3 being pushed into the working cylinder 1 slowly
• the third position (Fig. 9c) shows the piston rod 3 being pushed into the working cylinder 1 quickly.
• the moving piston 2 with sealing towards the "inner wall of the working cylinder 1 using an element 2a and joined with one end of the piston rod 3 is fitted on the working 1 cylinder as shown in Fig. 9a, the other end of the piston ro'd 3 protruding out of the working cylinder 1 through the annular bottom (not shown) .
• the piston 2 has axial holes 8, interconnecting the space above the piston 2 at the side of the piston rod 3 and the space below the piston 2 at the reverse side of the piston rod 3.
• the inner defining tube 12 is fitted on the piston rod 3
• the outer defining tube 11 is fitted on the inner defining tube 12.
• the axially-moving throttle ring 7 is fitted between the outer collar 13 made up on the end of the inner defining tube 12 and the end of the outer defining tube 11 near to the piston 2. The distance between the throttle ring 7 and axial holes 8 in the piston 2 can be adjusted by changing the axial position of the outer collar 13 on the inner defining tube 12 and the end of the outer "defining tube 11 on the piston rod 3.
• the throttle ring 7 opens or closes working medium flow through the axial holes 8.
• An additional throttle ring 60 is provided at the side of the piston 2 reverse to the piston rod 3.
• a coil spring 61 going through the axial hole 8, is fitted between the throttle ring 7 and the additional throttle ring 60.
• a pin 62 goes through the coil spring 61.
• One end of the pin 62 is fixed to the additional throttle ring 60 and the other end, going through the hole 63" in the throttle ring 7, has collar 64 at its end to define maximum distance between the throttle ring 60 and the throttle ring 7.
• the coil spring 61 pushes the throttle ring 60 and the throttle ring 7 away from one another, up to the maximum distance defined by the length of the pin 62.
• the piston 2 is connected with the end of the piston rod 3 via thread, allowing the piston 2 to be turned in relation to the piston 3, thus adjusting the mutual axial position, with the end of the piston rod 3 projecting from the piston 2 and the projected part of the piston rod 3 providing for an axial stop for the additional throttle ring 60.
• working medium flows through the axial holes 8 from the space above the piston 2 at the side of the piston rod 3 into the space below the piston 2 at the reverse side of the piston rod 3.
• working-medium pressure in the space above the piston 2 at the side of the piston rod 3 will exceed the pressure below the piston -2 at the reverse side of the piston rod 3.
• the entire assembly of the air spring as specified herein can be seen in Fig.10.
• the working cylinder 1 is closed at one side with the first bottom 4, which outer side has lugs 21 intended for connection with one suspended subject.
• the other side of the working cylinder 1 has an annularly-shaped hole 5.
• the sealed piston rod 3 goes through this hole.
• the free end of the piston rod 3, protruding from the working cylinder 1, has a lug 20 for connection with the other suspended subject.
• the piston 2 is fitted at the end of the piston rod 3, protruding into the working cylinder 1.
• the inner defining tube 12 with collar 13, outer defining tube 11, throttle ring 7, moving axially between the collar 13 on the inner defining tube 12 and the end of the outer defining tube 11, are fitted on the piston rod 3.
• Pins 62 fitted in the axial holes 8 in the piston 2 are fixed to the additional throttle ring 60 provided at the side of the piston 2, reverse to the piston rod 3, one end of the pins going through the holes 63 of the throttle ring 7 and having a collar at their ends and their other ends protruding out of the axial holes 8.
• Coil springs 61 going through the axial holes 8 are provided between the additional throttle ring 60 and throttle ring 7.
• the inner defining tube 12 is fitted in a thread made on the piston rod 3. By turning the inner defining tube 12 with the collar 13, the tube will move axially in relation to the piston rod 13 and piston 2.
• the outer defining tube 11 is fitted in a thread on the inner defining tube 12.
• the outer defining tube 11 in relation to the inner defining tube 12 will cause the outer defining tube 11 to move axially in relation to the inner defining tube 12 and piston rod 3.
• Axial movement of the outer defining tube 11 defines axial stop for movement of the throttle ring 7.
• the inner defining tube 12 is coupled with the bottom of the outer cylindrical link 19, and the outer defining tube 11 is coupled with the bottom of the inner cylindrical link 18-.
• Both the inner cylindrical link 18 and the outer cylindrical ' link 19 are fitted coaxially at the working cylinder 1.
• the radial guide pin 70 loosely fitted in recess 74 on surface of the inner cylindrical link 18 and the guide groove 75 provided in the outer cylindrical link 1'9 protrudes from the working cylinder 1.
• the working cylinder 1 is connected to one suspended subject (it cannot turn around its axis) .
• the piston rod 3 with the inner defining tube 12 and outer defining tube 11 will be pushed into the working cylinder 1, the radial pin 70 will turn the outer cylindrical link 19 and inner defining tube 12, thus moving the inner defining tube 12 in its thread on the piston rod 3 and allowing the collar 13 oh* the rod to define axial stop for the throttle ring 7.
• Fig. 11 in a view from above on the air spring as shown in Fig. 10, shows the radial 1' pin 71, also connected to the working cylinder 1, however, turned by 90°.
• the radial pin 71 is fitted in the guide groove 72 on the inner cylindrical link 18 and loosely fitted in recess 73 on surface of the outer cylindrical link 19.
• the radial pin 71 As the piston rod 3 with the inner defining tube 12 and the -outer defining tube 11 moves into the working cylinder 1, the radial pin 71, fitted in the guide groove 72, turns the inner link 17 and the outer defining tube 11, thus causing the end of the outer defining tube 11 to define axial stop for the throttle ring 7.
• Design of the air spring ' -as shown in Fig. 12 includes a spring unit proper, consisting, ⁇ ' f the working cylinder 1 with the first bottom 4, the piston 2 and piston rod 3, fitted in the sealed annular bottom 5, the rotating and sliding inner defining tube 12 fitted in a thread provided on the piston rod 3, the rotating and sliding outer defining tube 11 fitted in a thread provided on the i'f ⁇ her defining tube 12, the throttle ring 7 with axial holes, * " fitted between the collar 13 on the inner defining tube 12 and the end of the outer defining tube 11, the additional throttle ring 60 with pins 62 fitted in the axial holes of the piston- 1 2 and axial holes in the throttle ring 7, the coil springs ' 61 fitted between the additional throttle ring 60 and throttle ring 7.
• a spring unit proper consisting, ⁇ ' f the working cylinder 1 with the first bottom 4, the piston 2 and piston rod 3, fitted in the sealed annular bottom 5, the rotating and sliding inner defining tube 12 fitted in a thread provided on the piston rod 3,
• the inner defining tube 12 is fixed to the bottom" of the manually-operated cylindrical handle 19a, and the outer *' defining tube 11 is fixed to the bottom of the manually-operated cylindrical handle 18a.
• Turning cylindrical handles 18a, 19a allows axial movement of the inner defining tube 12 and outer defining tube 11, thus setting axial stops for movement of the throttle ring 7.
• the back valve 5 intended for. working medium flow into the working cylinder 1 is provided in the bottom 5 of the working cylinder 1.
• the working cylinder 1 goes through the bottom 205 of the outer working cylinder 201 and provides a piston of the outer working cylinder 20-1, closed by the first bottom 204 with lugs 21 intended for -.connection of a suspended subject.
• the back valve 210 intended for working medium flow into the working cylinder 201 is provided in the first bottom 204 of the outer working cylinder 201.
• Working medium pressure in the outer working cylinder 20-1 is higher than that in the working cylinder 1.
• working medium will be displaced from the space below the'?piston 2 between the first bottom 4 and piston 2 into the space above the piston 2 between the second bottom 5 and piston 2 and vice versa, working medium flow being throttled by the ring 7.
• Adequate adjustment of initial values of working medium pressure in the working cylinder 1 and outer working cylinder 201 allows setting of the moment at which the outer working cylinder 201 wili : 'start to work.
• the air spring design as shown in Fig. 12 allows setting of required behaviour of the spring when compression force of variable frequency and amplitude is applied on the spring (depending on parameters of the spring) .
• This design according to Fig. 12 can be implemented mainly in applications featuring high load applied on the air spring, e.g. i-ri" trucks .

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• 2009
  • 2009-02-02 WO PCT/CZ2009/000008 patent/WO2009094959A2/en not_active Ceased
  • 2009-02-02 EP EP09706207A patent/EP2250391A2/de not_active Withdrawn

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