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
  • F16F9/04—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum in a chamber with a flexible wall
  • F16F9/0445—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using gas only or vacuum in a chamber with a flexible wall characterised by intermediate rings or other not embedded reinforcing elements
• • 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
  • F16F7/00—Vibration-dampers; Shock-absorbers
  • F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
  • F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
  • F16F7/112—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on fluid springs

Definitions

• the present invention relates generally to air springs and more particularly, to an air spring having at least a pair of sleeves separated by a damping mass to provide vibration isolation, in which at least each of the sleeves has a rolling lobe which moves along a piston when the air spring is moving toward a compressed position.
• Pneumatic springs commonly referred to as air springs, have been used for motor vehicles for a number of years to provide cushioning between movable parts of the vehicle, primarily to absorb shock loads placed on the vehicle axle by the wheel striking an object in the road or falling into a depression.
• the air spring usually consists of a flexible rubber sleeve or bellows containing a supply of compressed fluid and has a pair of end members sealingly secured to the open ends of the bellows.
• one of the end members is a piston which causes compression and expansion of fluid within the bellows as the bellows compresses and expands as the vehicle experiences the road shock.
• the bellows is formed of a sufficient length in order to form a rolling lobe adjacent the piston, which lobe rolls along the side of the piston, especially during the air spring moving toward a compressed position.
• One problem that occurs in air springs is that a high frequency vibration develops as the air spring continually expands and contracts as the vehicle is in motion along a roadway. These high frequency vibrations are then transmitted to the vehicle causing a harsher ride.
• the present invention provides an air spring having an elastomeric bellows extending between a pair of end members wherein the bellows is divided into at least a pair of sleeves and subchambers by a vibration blocking mass to prevent high frequencies from being developed and transmitted to the vehicle.
• the air spring of the invention uses at least one piston which is connected to one of the dual sleeves, wherein the dual sleeve has a rolling lobe formed by the flexible sleeve which moves along the piston during compression of the air spring; and in which the piston can function as the blocking mass or be used in combination with a separate blocking mass at the midpoint of the elastomeric bellows when the piston is used as one of the end mounting member.
• Another aspect of the invention provides forming the bellows as a single one piece elongated flexible sleeve with inner and an outer metallic rings located generally at the midpoint of the bellows which clamp the flexible sleeve therebetween, with the rings functioning as the vibration blocking mass.
• a further feature of the invention provides an air spring in which a pair of pistons are mounted in an end-to-end abutting relationship, generally at the midpoint of the air spring bellows and divide the bellows into the pair of dual sleeves, each associated with one of the pistons, with end plates mounting the opposite ends of the air spring bellows to the spaced vehicle components.
• Another aspect of the invention is to provide a pair of opposed bell-shaped members extending outwardly from the blocking mass in opposite directions from the midpoint of the air spring to provide stabilizers for the spaced dual sleeves formed in the bellows.
• a further feature of the invention is that the location and construction of the blocking mass is at a positive position on the bellows, generally adjacent the midpoint thereof, and is secured in position either by functioning as end members of the dual sleeves or by being clamped in position by inner and outer rings which also function as part of the blocking mass.
• a still further feature of the invention is providing an air spring having at least three subchambers formed by a pair of spaced blocking masses with at least one of the end members being a piston along which a rolling lobe of the adjacent sleeve moves during collapsing of the air spring.
• FIG. 1 is a side elevational view of a first embodiment of the dual sleeve air spring containing vibration isolation;
• Fig. 2 is an elevational view with portions broken away in section, of the air spring of Fig. 1 ;
• Fig. 3 is a sectional view taken along line 3-3, Fig. 2;
• Fig. 4 is an elevational view with portions broken away in section, of a second embodiment of the dual sleeve air spring;
• Fig. 5 is a sectional view taken along line 5-5, Fig. 4;
• Fig. 6 is a elevational view with portions broken away and in section, of a third embodiment of the dual sleeve air spring
• Fig. 7 is a sectional view taken along line 7-7, Fig. 6;
• Fig. 8 is an elevational view with portions broken away and in section, of a fourth embodiment of the dual sleeve air spring;
• Fig. 9 is a sectional view taken along line 9-9, Fig. 8;
• Fig. 10 is an elevational view of a fifth embodiment of the dual sleeve air spring;
• Fig. 11 is an elevational view with portions broken away and in section, of the dual sleeve air spring of Fig. 10;
• Fig. 12 is a sectional view taken along line 12-12, Fig. 11;
• Fig. 13 is an elevational view with portions broken away and in section, of a sixth embodiment of the dual sleeve air spring
• Fig. 14 is a sectional view taken along line 14-14, Fig. 13;
• Fig. 15 is an elevational view of a seventh embodiment of the dual sleeve air spring;
• Fig. 16 is an elevational view with portions broken away in section, of the dual sleeve air spring of Fig. 15;
• Fig. 17 is a sectional view taken along line 17-17, Fig. 16; and Fig. 18 is an elevational view with portions broken away and in section, of another embodiment of the invention. DESCRIPTION OF THE PREFERRED EMBODIMENTS
• a first embodiment of the dual sleeve air spring of the present invention is indicated generally at 1 , and is shown in Figs. 1 -3.
• Air spring 1 is shown mounted between a pair of spaced structures 2 and 3, at least one of which is movable. Structures 2 and 3 usually are mounted on a vehicle and form part of a suspension system therefor.
• Air spring 1 includes an elongated bellows 4, which for embodiment 1 is a single elongated elastomeric member as shown in Fig. 2, usually containing reinforcing cords.
• Bellows 4 has a pair of open ends 5 and 6 which are sealingly connected by crimp rings 8 to stepped shoulders 9 of the terminal ends of a pair of similar pistons 10.
• Bellows 4 forms an internal pressure chamber 12 which is usually connected to a source of pressurized air (not shown) such as a compressor mounted on the vehicle which communicates with chamber 12 by an air line.
• Each piston 10 has an outer annular wall 14 which may be tapered inwardly toward its terminal end as shown in Fig. 2.
• Piston 10 has a bottom mounting surface 15 which is adapted to be placed on structures 2 and 3 and secured thereto by some type of usual fastener (not shown) such as bolts.
• Bellows 4 has a sufficient length in order to form a rolling lobe 16 adjacent the open ends, which lobes roll along outer surfaces 14 of pistons 10, especially as the air spring moves toward a compressed position wherein the pistons move toward each other to provide a desired damping characteristic to the air spring.
• a blocking mass indicated generally at 18, is mounted on and generally adjacent to the midpoint of bellows 4.
• mass 18 is formed by a pair of annular metallic rings 19 and 20 which matingly engage and clamp a midpoint 21 of bellows 4 therebetween.
• Blocking mass 18 divides bellows 4 into a pair of flexible dual sleeves 23 and 24, which in turn divide pressure chamber 12 into a pair of dual subchambers 26 and 27 respectively.
• air spring 1 is provided with a pair of dual sleeves 23 and 24 having a centrally located blocking mass 18, and most importantly has a pair of pistons 10 along which rolling lobes 16 move, as the air spring moves toward a compressed position.
• the dual pistons and sleeves provide improved damping characteristics in addition to the vibration isolation provided by mass 18.
• Mass 18 permits fluid communication between the dual subchambers since the entire center portion of ring 20 is open between the subchambers.
• Air spring 30 includes bellows 4 which is formed of a single one piece elastomeric material and a pair of end mounting pistons 10.
• the central blocking mass indicated generally at 31 divides bellows 4 into the dual sleeves 23 and 24 and subchambers 26 and 27.
• Blocking mass 31 includes inner clamping ring 20 and an outer annular stabilizing member 33. Stabilizing member
• 33 preferably is formed as a one piece metal member and includes a central ring
• Air spring 30 is provided with a central vibration blocking mass 31 formed by inner clamp ring 20 and outer stabilizing member 33, which mass prevents the accumulation and transmission of high vibration frequency, and which includes pistons 10 along which lobes 16 move, especially as the air spring moves towards a compressed condition.
• Air spring 40 includes pistons 10 which are secured to structures 2 and 3 and which engage rolling lobes 16 as discussed previously above with respect to air springs 1 and 30.
• the bellows of air spring 40 is formed by two separate sleeves 41 and 42 instead of the single continuous member of bellows 4. Inner open ends 43 and 44 of sleeves 41 and 42 respectively, are sealingly clamped by annular outer bands 46 and 47 against annular flanges 48a and 49a extending outwardly from the periphery of a pair of end plates 48 and 49 respectively.
• End plates 48 and 49 have a disc-like configuration and have aligned central openings 48c and 49c to provide fluid communication between subchambers 26 and 27 formed by sleeves 41 and 42 respectively.
• end plates 48 and 49 which are formed of metal, provide the blocking mass 39 for the vibration frequency isolation and are secured together by welds 45, bolts or other type of fastening means.
• the pair of end pistons 10 provide the desired damping effect with intermediate blocking mass 39 providing the high frequency vibration blocking in improved air spring 40.
• fluid communication is provided between the subchambers through the center opening 48c and 49c of end plates 48 and 49.
• a fourth embodiment of the air spring is indicated generally at 50, and is shown in Figs. 8 and 9.
• Air spring 50 is very similar to embodiment 40 except that disc-shaped end members 51 and 52, which are abuttingly joined together by welds 54 or other type of fastening means, to provide the central high frequency blocking mass 53, are solid disc-shaped plates free of any openings so that subchambers 26 and 27 are fluidly independent of each other.
• the remaining features of air spring 50 are similar to that described above for air spring 40, and thus are not discussed in further detail.
• a fifth air spring embodiment is indicated generally at 60, and is shown in
• Air spring 60 includes the pair of separate elastomeric sleeves 41 and 42 which form subchambers 26 and 27, respectively. Opposite open ends 61 and 62 of sleeves 41 and 42, respectively, are sealingly clamped against annular peripheral flanges 63 and 64 of disc-shaped end plates 65 and 66 by annular outer bands 65a and 66a, which in turn are secured to spaced structures 2 and 3, respectively.
• pistons 10 are mounted in an end-to-end abutting relationship and are rigidly secured together by welds 65 or other type of fastening means, such as bolts, brackets, etc. Again, the open ends of sleeves 41 and 42 are sealingly connected to stepped shoulders 9 of the terminal ends of pistons 10 by clamp rings 8.
• pistons 10 in addition to providing the outer tapered surfaces 14 along which rolling lobes 16 move, provide the high frequency vibration blocking mass 67. As shown in Fig. 11 , each piston 10 includes a central wall 66 which extends across the piston and prevents the passage of fluid between chambers 26 and 27.
• a sixth embodiment of the improved air spring is indicated generally at 70, and is shown in Figs. 13 and 14 and is very similar to embodiment 60 with the main difference being that the interiors of pistons 10 are free of a central wall 66 and are formed with a pair of central openings 71 which form a fluid passage 72 extending between subchambers 26 and 27 to permit the flow of fluid within the air spring between the subchambers. Again, the base ends of air springs 10 are secured together by welds 74 or other type of fasteners.
• a seventh embodiment of the improved air spring is indicated generally at
• Embodiment 80 includes a pair of pistons 10 which are adapted to be mounted on spaced structural structures 2 and 3, and includes clamping rings 8 which provides for a fluid seal adjacent the open ends of dual sleeves 41 and 42 which form fluid subchambers 26 and 27.
• the high frequency blocking mass indicated generally at 82 includes a pair of bell-shaped members 83 and 84 which include annular cup-shaped peripheral flanges 85a and 86a formed on and extending outwardly from annular bands 85 and 86, respectively.
• Annular bands 85 and 86 clamp the open ends of sleeves 41 and 42 against peripheral flanges 49a and 48a respectively, of end plate 49 and 48 as discussed above for air spring 40 (Fig. 6).
• Plates 48 and 49 are joined by welds 87 or other fasteners into the abutting relationship as shown in Fig. 16. As shown in Fig. 16, end plates 48 and 49 have central openings 48c and 49c which align with each other to provide a central passage extending between dual subchambers 26 and 27.
• Bell-shaped members 83 and 84 including bands 85 and 86, are formed of metal and provide the high frequency blocking mass 82 located at the midpoint of the fluid pressure chamber formed by sleeves 41 and 42 with pistons 10 being the end mounting members for mounting the air spring on spaced structures 2 and 3.
• Air spring 90 includes a piston 10 at its lower end which is secured to structure 3 and an end plate 66 at its upper end for mounting the air spring on structure 2. End plate 66 is sealingly secured by annular band 66a to the open end of bellows 4. The unique feature of embodiment 90 is that two blocking masses 92 and 93 are mounted on bellows 4.
• Each blocking mass includes outer and inner rings 19 and 20 which divide the internal pressure chamber into three separate subchambers 94, 95 and 96 which are in fluid communication with each other as shown in Fig. 18.
• Air spring 90 is nonsymmetrical in that it has a single piston at one end and an end plate at the opposite end for mounting the air spring on spaced structures 2 and 3, and has three separate subchambers formed by the pair of spaced blocking masses. It is readily understood that if desired, three or more blocking masses could be utilized spaced at different intervals, either equally distant or nonequally distant from each other, dividing the air spring into a plurality of subchambers as well as providing a piston at each end as the mounting members without affecting the concept of the invention.
• embodiment 90 is provided with a blocking mass in combination with a piston engageable with a rolling lobe to eliminate the high frequency vibrations while still providing the advantages of a rolling lobe/piston damping action.
• each of the various air spring embodiments described above provides an air spring having a central blocking mass formed of a weighted material which prevents the development and/or transmission of high vibration frequencies to the spaced structures.
• Each air spring is provided with a pair of pistons, either at the end mounting locations with structures 2 and 3, or in the center of the air spring bellows, which in such constructions will also function as the blocking mass.
• no prior art air spring having a high frequency vibration blocking mass is provided with the dual subchambers either fluidly separated from each other or connected by a fluid passage chamber, in combination with a pair of pistons along which a pair of rolling lobes move as the air spring moves particularly toward a collapsed position to provide the desired vibration damping effect. While the embodiments of the invention have been described, the invention imited thereto. The claims of the invention follow.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Fluid-Damping Devices (AREA)

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Cited By (13)

Citations (8)

• 2001
  • 2001-08-27 WO PCT/US2001/026705 patent/WO2002040888A1/en active Application Filing
  • 2001-08-27 AU AU2001286821A patent/AU2001286821A1/en not_active Abandoned
  • 2001-09-26 AR ARP010104542 patent/AR034154A1/es unknown

Patent Citations (8)

Non-Patent Citations (1)

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