CA2008354A1 - Surface bearing and method for its production - Google Patents
Surface bearing and method for its productionInfo
- Publication number
- CA2008354A1 CA2008354A1 CA002008354A CA2008354A CA2008354A1 CA 2008354 A1 CA2008354 A1 CA 2008354A1 CA 002008354 A CA002008354 A CA 002008354A CA 2008354 A CA2008354 A CA 2008354A CA 2008354 A1 CA2008354 A1 CA 2008354A1
- Authority
- CA
- Canada
- Prior art keywords
- hollow channels
- surface bearing
- hollow
- bearing
- cavities
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
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
- F16F1/00—Springs
- F16F1/36—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers
- F16F1/373—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape
- F16F1/377—Springs made of rubber or other material having high internal friction, e.g. thermoplastic elastomers characterised by having a particular shape having holes or openings
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B29—WORKING OF PLASTICS; WORKING OF SUBSTANCES IN A PLASTIC STATE IN GENERAL
- B29C—SHAPING OR JOINING OF PLASTICS; SHAPING OF MATERIAL IN A PLASTIC STATE, NOT OTHERWISE PROVIDED FOR; AFTER-TREATMENT OF THE SHAPED PRODUCTS, e.g. REPAIRING
- B29C33/00—Moulds or cores; Details thereof or accessories therefor
- B29C33/44—Moulds or cores; Details thereof or accessories therefor with means for, or specially constructed to facilitate, the removal of articles, e.g. of undercut articles
- B29C33/48—Moulds or cores; Details thereof or accessories therefor with means for, or specially constructed to facilitate, the removal of articles, e.g. of undercut articles with means for collapsing or disassembling
- B29C33/485—Moulds or cores; Details thereof or accessories therefor with means for, or specially constructed to facilitate, the removal of articles, e.g. of undercut articles with means for collapsing or disassembling cores or mandrels
Abstract
ABSTRACT OF THE DISCLOSURE
The invention relates to a surface bearing 1 comprising a rubber strip or plate material penetrated by hollow channels and cavities. The cavities and hollow channels all lie in a single plane at least essentially parallel or complementary in shape to the principal surface of the sheet material, each cavity being penetrated in each case by only one hollow channel 3. The hollow channels are open on at least one side and have a clear cross-sectional area which is at least a quarter of the largest cross-sectional area of the cavities penetrated by said hollow channel.
The hollow channels can extend non-parallel to at least one longitudinal axis or to the longitudinal axis of the surface bearing, thus, for example, can form an angle of 90 or 45° with the latter, while they are parallel or non-parallel to one another. However, in the case of polygonal or circular surface bearings, they can also be aligned so as to extend radially to the center, without intersecting or touching in the center, i.e.
can also be open on only one side. An opening formed in the center of the surface bearing does not impair the bearing properties, instead offering numerous constructional possibilities. Overall, cushioning soft of heavy loads, free from the buckling effect, is obtained, substantial acoustic decoupling being achieved.
The invention relates to a surface bearing 1 comprising a rubber strip or plate material penetrated by hollow channels and cavities. The cavities and hollow channels all lie in a single plane at least essentially parallel or complementary in shape to the principal surface of the sheet material, each cavity being penetrated in each case by only one hollow channel 3. The hollow channels are open on at least one side and have a clear cross-sectional area which is at least a quarter of the largest cross-sectional area of the cavities penetrated by said hollow channel.
The hollow channels can extend non-parallel to at least one longitudinal axis or to the longitudinal axis of the surface bearing, thus, for example, can form an angle of 90 or 45° with the latter, while they are parallel or non-parallel to one another. However, in the case of polygonal or circular surface bearings, they can also be aligned so as to extend radially to the center, without intersecting or touching in the center, i.e.
can also be open on only one side. An opening formed in the center of the surface bearing does not impair the bearing properties, instead offering numerous constructional possibilities. Overall, cushioning soft of heavy loads, free from the buckling effect, is obtained, substantial acoustic decoupling being achieved.
Description
~200~3~
The present inven-tion relates to a surface bearing comprising a rubber strip or plate material penetrated by hollow channels and cavities. The cavities and hollow channels all lie in a single plane at least essentially parallel or complementary in shape to the principal surface of the bearing, each cavity being penetrated in each case by only one ]hollow channel.
Resilient surface bearings of this kind are generally used for cushioning relatively large masses, e.g. in mattress and machine construction, the soft cushioning of drive assemblies and engines of motor vehicles with little noise being o~ particular interest.
The achievement o~ a good combination of the effects of soft springing, i.e. of a shallow spring characteristic, as long a service life as possible and good acoustic decoupling, has always presented difficulties since, on the one hand, the material used should not be too hard and, on the other hand, the mechanical stressability and durability should not be too low. A further economic aspect is, in addition, the expenditure involved in production.
The previously used solid elastomer pads of relatively soft materials, in which rapld material fatique was to be observed, have nowadays largely been replaced by bearings which are penetrated by hollow channels and cavities to reduce material loading. When the bearing is loaded, the cavities accommodate displaced elastomer material, while the hollow channels serve to connect the cavities, a pressure compensatlon thereby being made possible between said cavities.
In general, when used correctly, surface bearings are sub;ect to only relatively small loads per unit area. However, as soon as higher loads occur, the cavity walls buckle (buckling effect)~the Z0~83~i~
restoring force thereby largely being lost. The spring characteristic then has a horizontal or, in most cases, falling gradient. As soon as the cavities present have been completely compressed, the shallow reglon of proportionality makes a rapid transition to the progressivP region with a steeply rising characteristic. The bearing then shows the typical, here undesired, behaviour of a solid elastomer pad.
Bearings whose cavities and channels are filled with a fluid, are described as dampers. A bearing o~ this kind, the cavities oE
which are filled with a damping fluid, the effect of a hydraulic surface damper thereby being achieved, is disclosed in Japanese Laid-Open Specification JP 52 37675 A and is used in the known form as, inter alia, a rebound wall or rail support. In this surface damper, the cavities are designed as vertical cylinders, i.e. the cylinder axes extend in the direction of the applied-load vector. In the case of the strip-like embodiment, these cylinder cavities are connected to one another by linear restrictor channels or in the case of the sheet-like configuration are connected by a hexagonal restrlctor-channel network, i.e. three channels penetrate each hollow cylinder.
A connection of this type between the cavities permits the damping fluid to overflow out of the loaded cavities into the unloaded and/or less loaded cavities, which are thereby expanded by virtue of the elasticity of the bearing material, as a result of which the materlal loading is reduced due to the reduction in the inhomogeneous stress concentration.
Disadvantages of bearings of this type are that the fluid-filled and thus resiliently reinforced dampers, which are closed all round, do not respond to high frequency low amplitude oscillat~ons and hence work relatively noisily and that, due to the inertia caused, inter alia, by the narrow restrictor channels, which is associated with great elastomer compression and thus a relatively steep rise in the spring characteristic, ~ 335i4 desirably soft cushioning is not possible to the desired extent unless a softer materlal were used, although this in turn would considerably shorten the service life.
A further disadvantage is that, due to the adhesively bonded laminated structures, the production of bearings of this kind is expensive in terms of time, production and personnel and hence has to be carried out in a cost-intensive way.
The present invention provides a surface bearing from a durable, relatively firm elastic material~ which is suitable for cushioning high loads as stipulated and which nevertheless has a shallow spring characterlstic over a wide restorlng range, i.e.
has a soft spring characteristic, which furthermore permits good acoustic decoupling and long service lives with undiminished functioning capacity and, in addition, can be produced easily, rapidly and economically.
According to the present invention there is provided a surface bearing comprising a rubber strip or plate having in the rubber matrix a plurality of hollow channels and cavities all of which lie in a single plane at least essentially parallel to the principal surface of the sheet material or complemtary in shape to said principal surface, each cavity being penetrated in each case by only a single hollow channel, wherein the hollow channels are open on at least one side and have a clear cross-section, the area of which is at least 1/4 of the size of the largest cross-sectional area of the nearest cavity penetrated by this hollow channel. Thus according to the present invention the hollow channels are open on at least one side and have a clear cross-section, the area of which is at least one ~uarter of the size of the largest cross-sectional area of the nearest cavity penetrated by this hollow channel.
The surface bearing comprises a rubber strip or a rubber plate, in which uniformly distributed cavities and hollow channels are ~no835~
formed which all lie in a single plane a-t least essentially parallel or complementary in shape to the principal surface of the surface bearing. Each cavity of the rubber matrix is penetrated by only one of the hollow channels, which preferably extend rectilinearly and are open on at least one side. In the preferred embodiment, the cavities are of spherical or spheroidal design, while the hollow channels preferably have a circular cylindrical form. In partlcular, al:l cavities and hollow channels are arranged ln such a way that the center of each ~o spherical cavity lies on the central axis of the hollow channel intersecting this cavity.
Essential here is that the hollow channels, which nei~her intersect nor touch, have a clear cross-section, the area of which ls at least a quarter of the size of the greatest cross-sectional area of the nearest cavity penPtrated by this hollow channel.
By means of this cross-section ratio it is ensured that, overall, a sufficiently large hollow volume ls available inside the surface bsaring, which can accommodate the displaced rubber material when the bearing body is compressed without extreme material stresses arising. The channels thus do not ~unction as restrictor channels but themselves represent a deflection space for the rubbermaterial, resulting in a softening of the surface bearing and a shallower spring characteristic. Due to the uniform distributlon of the cavities and channels in the matrix of the surface bearing, the mechanical strength of the bearing body is not impaired despite the remarkable pore volume and, even under considerable applied loads, has a long service life. ~he deformation stresses occurring upon loading, which primarily affect the free internal and external surfaces of the rubber mairix, are distributed uniformly over the entire bearing body, with the result that, even when the bearing consists of a relatively firm and mechanically stable engineerin~ material, the ~3~83'S~
sprlng characteristic is decidedly soft and the sprlng characteristlc accordingly has a broad and shallow region of proportionality and makes the transition into the progressive region with moderate curvature under only a relatively high load.
In preferred embodiments of the invention, the hollow channels are aligned in such a way that they extend nonparallel to at least one or to the longitudinal principal axis of the sheet material and preferably enclose an angle of go or 45 with said axis, the channels being open on one or both sldes. In the case of the channels open on only one side, the openings preferably lie alternately on the in each case opposite sides of the sheet material.
The channels here extend parallel to one another or form a plurality of groups of in each case mutually parallel channels, the central axes of which intersect one another without the hollow channels themselves intersecting or touching, thus for example forming a herringbone pattern.
Alternatively, in the case of an essentially regularly polygonal or circular sheet material, the hollow channels can be aligned so as to extend radially to the center, although they neither intersect nor touch in the center and are thus only open on one side.
In the center of the novel surface bearing it is furthermore possible for an opening to be formed which, extending in the direction of the normal to the principal surface, i.e. in the direction of the applied-load vector, is a through opening or an opening closed on one side in the manner of a blind hole or a groove, none of the cavities or hollow chann21s opening into this central channel. A central opening of this kind permits numerous constructional possibilities, e.g. fixing possibilities.
Additional lateral stabilization can be achieved by means of a stabilizing or guide rod passed through this opening. In this arrangement, the spring or acoustic properties of the bearlng are in no way diminished.
Also surprising, overall, is the fact that, even ln the case of a relatively shallow surface bearing penetrated in a single layer by cavities and hollow channels, mar]cedly good spring properties and substantial acoustlc decoupling can already be achieved.
The novel surface bearing is produced by compresslon molding or in~ection molding of rubber blends in a mold cavity contalning mold cores. After the solidification of the elastomer mass, the reusable mold cores, consisting, for example, of steel, are removed from the mold cavity together with the molding, i.e. the molding is demolded. The rod-shaped mold cores, which are provided at regular intervals with thickened portions, are pulled out laterally, individually or in groups, from the molding. The surface-bearing obtained is then immediately ready for use, the surface-bearings of engines or drives assemblies of motor vehicles being envisaged in particular as applicat~ons.
The invention is explained in greater detail below with reference to the accompanying drawings in which:
Fig. l shows, in schematic representation, a horizontal sectlon through a surface bearing according to the first embodiment of the invention;
Fig. 2 shows the bearing according to Fig. l in side view;
Fig. 3 shows a vertical section in accordance with III-III in Fig. l;
Fig. 4 shows, in schematlc representation, a horizontal section through a second embodiment of the bearing according to the invention;
~0~533S~
Fig. 5 shows, in schematlc representa-tion, a horizontal section through a thlrd embodiment of the novel bearing; and Fig. 6 shows a vertical section in accordance with VI-VI in Fig.
5 5.
In the surface bearing 1 shown in Fiqs. 1 to 3, the cavities 2 formed in the rubber matrix and the hollow channels 3 are dlstributed in su~h an arrangement that, as can be seen in particular in Figs. 2 and 3, they lie in a single plane parallel or complementary in shape to the principal surface of the sheet material.
The channels 3 extend at an anyle of 90 to the longitudinal axis lS of the bearing, which in the drawing is oriented from the top to the bottom, parallel to one another, and are open on one side and alternately towards the opposite sides of the bearing body 1.
Preferably, the spacing between the individual channels 3 is of equal size in each case. Each channel 3 penetrates a plurality of cavities 2, which are preferably at equal distances from one another, while, conversely, each cavity 2 is only penetrated by a single channel 3. The cross-sectional area of the circular cylindrical channels 3 is at least a quarter of the largest cross-sectional area of the spherical cavlties 2, thP centers 4 of the cavities 2 lying on the central axis 5 of the respective channel 3.
In contrast, the surface bearing 1 shown in Fig. 4 has hollow channels 3 which extend at an angle of 45 to the longitudinal axis of the bearing and are open on both sides.
The novel surface bearing 1 shown in Figs. 5 and 6 comprises a cir~ular sheet material in which the hollow channels 3 are once again formed so as to be open on only one side and extend radially towards the center. However, their length is such that they do not quite reach the opening 6 which i9 present in the 335~
center and extends in the direction o~ the normal to the principal surface, i.e. do not open into said opening. The central hole channel 6 is open on both sides, i.e. passes through the surface bearing 1 over its entire thickn~ss.
Given correct use, the surface bearings 1 shown in the accompanying drawings are loaded in t:he dlrection of the normal to the principal surface, the elastomer material displaced being accommodated by the cavities 2 and the channels 3 or even 6. A
soft spring acttion, free from the buckling effect, and good acoustic decoupling are thereby obtained. The demands made on surface bearings for engines in automotive construction are here ful~illed in all respects.
The present inven-tion relates to a surface bearing comprising a rubber strip or plate material penetrated by hollow channels and cavities. The cavities and hollow channels all lie in a single plane at least essentially parallel or complementary in shape to the principal surface of the bearing, each cavity being penetrated in each case by only one ]hollow channel.
Resilient surface bearings of this kind are generally used for cushioning relatively large masses, e.g. in mattress and machine construction, the soft cushioning of drive assemblies and engines of motor vehicles with little noise being o~ particular interest.
The achievement o~ a good combination of the effects of soft springing, i.e. of a shallow spring characteristic, as long a service life as possible and good acoustic decoupling, has always presented difficulties since, on the one hand, the material used should not be too hard and, on the other hand, the mechanical stressability and durability should not be too low. A further economic aspect is, in addition, the expenditure involved in production.
The previously used solid elastomer pads of relatively soft materials, in which rapld material fatique was to be observed, have nowadays largely been replaced by bearings which are penetrated by hollow channels and cavities to reduce material loading. When the bearing is loaded, the cavities accommodate displaced elastomer material, while the hollow channels serve to connect the cavities, a pressure compensatlon thereby being made possible between said cavities.
In general, when used correctly, surface bearings are sub;ect to only relatively small loads per unit area. However, as soon as higher loads occur, the cavity walls buckle (buckling effect)~the Z0~83~i~
restoring force thereby largely being lost. The spring characteristic then has a horizontal or, in most cases, falling gradient. As soon as the cavities present have been completely compressed, the shallow reglon of proportionality makes a rapid transition to the progressivP region with a steeply rising characteristic. The bearing then shows the typical, here undesired, behaviour of a solid elastomer pad.
Bearings whose cavities and channels are filled with a fluid, are described as dampers. A bearing o~ this kind, the cavities oE
which are filled with a damping fluid, the effect of a hydraulic surface damper thereby being achieved, is disclosed in Japanese Laid-Open Specification JP 52 37675 A and is used in the known form as, inter alia, a rebound wall or rail support. In this surface damper, the cavities are designed as vertical cylinders, i.e. the cylinder axes extend in the direction of the applied-load vector. In the case of the strip-like embodiment, these cylinder cavities are connected to one another by linear restrictor channels or in the case of the sheet-like configuration are connected by a hexagonal restrlctor-channel network, i.e. three channels penetrate each hollow cylinder.
A connection of this type between the cavities permits the damping fluid to overflow out of the loaded cavities into the unloaded and/or less loaded cavities, which are thereby expanded by virtue of the elasticity of the bearing material, as a result of which the materlal loading is reduced due to the reduction in the inhomogeneous stress concentration.
Disadvantages of bearings of this type are that the fluid-filled and thus resiliently reinforced dampers, which are closed all round, do not respond to high frequency low amplitude oscillat~ons and hence work relatively noisily and that, due to the inertia caused, inter alia, by the narrow restrictor channels, which is associated with great elastomer compression and thus a relatively steep rise in the spring characteristic, ~ 335i4 desirably soft cushioning is not possible to the desired extent unless a softer materlal were used, although this in turn would considerably shorten the service life.
A further disadvantage is that, due to the adhesively bonded laminated structures, the production of bearings of this kind is expensive in terms of time, production and personnel and hence has to be carried out in a cost-intensive way.
The present invention provides a surface bearing from a durable, relatively firm elastic material~ which is suitable for cushioning high loads as stipulated and which nevertheless has a shallow spring characterlstic over a wide restorlng range, i.e.
has a soft spring characteristic, which furthermore permits good acoustic decoupling and long service lives with undiminished functioning capacity and, in addition, can be produced easily, rapidly and economically.
According to the present invention there is provided a surface bearing comprising a rubber strip or plate having in the rubber matrix a plurality of hollow channels and cavities all of which lie in a single plane at least essentially parallel to the principal surface of the sheet material or complemtary in shape to said principal surface, each cavity being penetrated in each case by only a single hollow channel, wherein the hollow channels are open on at least one side and have a clear cross-section, the area of which is at least 1/4 of the size of the largest cross-sectional area of the nearest cavity penetrated by this hollow channel. Thus according to the present invention the hollow channels are open on at least one side and have a clear cross-section, the area of which is at least one ~uarter of the size of the largest cross-sectional area of the nearest cavity penetrated by this hollow channel.
The surface bearing comprises a rubber strip or a rubber plate, in which uniformly distributed cavities and hollow channels are ~no835~
formed which all lie in a single plane a-t least essentially parallel or complementary in shape to the principal surface of the surface bearing. Each cavity of the rubber matrix is penetrated by only one of the hollow channels, which preferably extend rectilinearly and are open on at least one side. In the preferred embodiment, the cavities are of spherical or spheroidal design, while the hollow channels preferably have a circular cylindrical form. In partlcular, al:l cavities and hollow channels are arranged ln such a way that the center of each ~o spherical cavity lies on the central axis of the hollow channel intersecting this cavity.
Essential here is that the hollow channels, which nei~her intersect nor touch, have a clear cross-section, the area of which ls at least a quarter of the size of the greatest cross-sectional area of the nearest cavity penPtrated by this hollow channel.
By means of this cross-section ratio it is ensured that, overall, a sufficiently large hollow volume ls available inside the surface bsaring, which can accommodate the displaced rubber material when the bearing body is compressed without extreme material stresses arising. The channels thus do not ~unction as restrictor channels but themselves represent a deflection space for the rubbermaterial, resulting in a softening of the surface bearing and a shallower spring characteristic. Due to the uniform distributlon of the cavities and channels in the matrix of the surface bearing, the mechanical strength of the bearing body is not impaired despite the remarkable pore volume and, even under considerable applied loads, has a long service life. ~he deformation stresses occurring upon loading, which primarily affect the free internal and external surfaces of the rubber mairix, are distributed uniformly over the entire bearing body, with the result that, even when the bearing consists of a relatively firm and mechanically stable engineerin~ material, the ~3~83'S~
sprlng characteristic is decidedly soft and the sprlng characteristlc accordingly has a broad and shallow region of proportionality and makes the transition into the progressive region with moderate curvature under only a relatively high load.
In preferred embodiments of the invention, the hollow channels are aligned in such a way that they extend nonparallel to at least one or to the longitudinal principal axis of the sheet material and preferably enclose an angle of go or 45 with said axis, the channels being open on one or both sldes. In the case of the channels open on only one side, the openings preferably lie alternately on the in each case opposite sides of the sheet material.
The channels here extend parallel to one another or form a plurality of groups of in each case mutually parallel channels, the central axes of which intersect one another without the hollow channels themselves intersecting or touching, thus for example forming a herringbone pattern.
Alternatively, in the case of an essentially regularly polygonal or circular sheet material, the hollow channels can be aligned so as to extend radially to the center, although they neither intersect nor touch in the center and are thus only open on one side.
In the center of the novel surface bearing it is furthermore possible for an opening to be formed which, extending in the direction of the normal to the principal surface, i.e. in the direction of the applied-load vector, is a through opening or an opening closed on one side in the manner of a blind hole or a groove, none of the cavities or hollow chann21s opening into this central channel. A central opening of this kind permits numerous constructional possibilities, e.g. fixing possibilities.
Additional lateral stabilization can be achieved by means of a stabilizing or guide rod passed through this opening. In this arrangement, the spring or acoustic properties of the bearlng are in no way diminished.
Also surprising, overall, is the fact that, even ln the case of a relatively shallow surface bearing penetrated in a single layer by cavities and hollow channels, mar]cedly good spring properties and substantial acoustlc decoupling can already be achieved.
The novel surface bearing is produced by compresslon molding or in~ection molding of rubber blends in a mold cavity contalning mold cores. After the solidification of the elastomer mass, the reusable mold cores, consisting, for example, of steel, are removed from the mold cavity together with the molding, i.e. the molding is demolded. The rod-shaped mold cores, which are provided at regular intervals with thickened portions, are pulled out laterally, individually or in groups, from the molding. The surface-bearing obtained is then immediately ready for use, the surface-bearings of engines or drives assemblies of motor vehicles being envisaged in particular as applicat~ons.
The invention is explained in greater detail below with reference to the accompanying drawings in which:
Fig. l shows, in schematic representation, a horizontal sectlon through a surface bearing according to the first embodiment of the invention;
Fig. 2 shows the bearing according to Fig. l in side view;
Fig. 3 shows a vertical section in accordance with III-III in Fig. l;
Fig. 4 shows, in schematlc representation, a horizontal section through a second embodiment of the bearing according to the invention;
~0~533S~
Fig. 5 shows, in schematlc representa-tion, a horizontal section through a thlrd embodiment of the novel bearing; and Fig. 6 shows a vertical section in accordance with VI-VI in Fig.
5 5.
In the surface bearing 1 shown in Fiqs. 1 to 3, the cavities 2 formed in the rubber matrix and the hollow channels 3 are dlstributed in su~h an arrangement that, as can be seen in particular in Figs. 2 and 3, they lie in a single plane parallel or complementary in shape to the principal surface of the sheet material.
The channels 3 extend at an anyle of 90 to the longitudinal axis lS of the bearing, which in the drawing is oriented from the top to the bottom, parallel to one another, and are open on one side and alternately towards the opposite sides of the bearing body 1.
Preferably, the spacing between the individual channels 3 is of equal size in each case. Each channel 3 penetrates a plurality of cavities 2, which are preferably at equal distances from one another, while, conversely, each cavity 2 is only penetrated by a single channel 3. The cross-sectional area of the circular cylindrical channels 3 is at least a quarter of the largest cross-sectional area of the spherical cavlties 2, thP centers 4 of the cavities 2 lying on the central axis 5 of the respective channel 3.
In contrast, the surface bearing 1 shown in Fig. 4 has hollow channels 3 which extend at an angle of 45 to the longitudinal axis of the bearing and are open on both sides.
The novel surface bearing 1 shown in Figs. 5 and 6 comprises a cir~ular sheet material in which the hollow channels 3 are once again formed so as to be open on only one side and extend radially towards the center. However, their length is such that they do not quite reach the opening 6 which i9 present in the 335~
center and extends in the direction o~ the normal to the principal surface, i.e. do not open into said opening. The central hole channel 6 is open on both sides, i.e. passes through the surface bearing 1 over its entire thickn~ss.
Given correct use, the surface bearings 1 shown in the accompanying drawings are loaded in t:he dlrection of the normal to the principal surface, the elastomer material displaced being accommodated by the cavities 2 and the channels 3 or even 6. A
soft spring acttion, free from the buckling effect, and good acoustic decoupling are thereby obtained. The demands made on surface bearings for engines in automotive construction are here ful~illed in all respects.
Claims (11)
1. A surface bearing comprising a rubber strip or plate having in the rubber matrix a plurality of hollow channels and cavities all of which lie in a single plane at least essentially parallel to the principal surface of the sheet material or complementary in shape to said principal surface, each cavity being penetrated in each case by only a single hollow channel, wherein the hollow channels are open on at least one side and have a clear cross-section, the area of which is at least 1/4 of the size of the largest cross-sectional area of the nearest cavity penetrated by this hollow channel.
2. A surface bearing as claimed in claim 1, wherein the cavities have a spherical shape, the hollow channels are of circular cylindrical configuration, and the center of each spherical cavity lies on the central axis of the hollow channel intersecting said cavity.
3. A surface bearing as claimed in claim 2, wherein the hollow channels are aligned in a sheet material having at least one longitudinal principal axis in such a way that they extend nonparallel to said principal axis or to one of these longitudinal axes of the sheet material.
4. A surface bearing as claimed in claim 3, in which the hollow channel defines an angle of 90° or 45° with said longitudinal axis.
5. A surface bearing as claimed in claim 1, 2 or 3, wherein all hollow channels extend parallel to one another.
6. A surface bearing as claimed in claim 1, 2 or 3, wherein a plurality of groups of hollow channels extend parallel to one another, the central axes of said hollow channels intersecting one another without the hollow channels themselves intersecting.
7. A surface bearing as claimed in claim 1, 2 or 3, wherein all hollow channels are open on only one side, in such a way that the open sides of the hollow channels lie alternately on different sides of the sheet material.
8. A surface bearing as claimed in claim 1 wherein the plate is at least essentially regularly polygonal or circular sheet and all hollow channels are open on only one side and extend radially to the center of the sheet material without intersecting or touching in the center of said sheet material.
9. A surface bearing as claimed in claim 8 wherein an opening, which is a through opening or is closed on one side as a blind hole or a groove, is formed so as to extend in the center of the sheet material in the direction of the normal to the principal surface.
10. A method of producing surface bearings as claimed in claim 1, 2 or 3 by compression molding or injection molding of rubber blends in a mold cavity containing mold cores, wherein the molding, containing reusable mold cores is first of all removed completely from the mold together with the mold cores and wherein the mold cores are only then pulled out laterally, individually or in groups, the ready-to-use surface bearing thereby being obtained.
11. The use of the surface bearing as claimed in claim 1, 2 or 3 for surface-bearing the engine or the drive assembly of a motor vehicle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DEP3901898.9 | 1989-01-23 | ||
| DE3901898A DE3901898A1 (en) | 1989-01-23 | 1989-01-23 | AREA STORAGE AND METHOD FOR THE PRODUCTION THEREOF |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2008354A1 true CA2008354A1 (en) | 1990-07-23 |
Family
ID=6372621
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002008354A Abandoned CA2008354A1 (en) | 1989-01-23 | 1990-01-23 | Surface bearing and method for its production |
Country Status (7)
| Country | Link |
|---|---|
| EP (1) | EP0379689B1 (en) |
| JP (1) | JPH02229927A (en) |
| BR (1) | BR9000250A (en) |
| CA (1) | CA2008354A1 (en) |
| DE (2) | DE3901898A1 (en) |
| ES (1) | ES2039820T3 (en) |
| MX (1) | MX172663B (en) |
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| CN111872015A (en) * | 2020-06-01 | 2020-11-03 | 许昌学院 | Magnetic pulse mineralized refuse treatment device |
| EP3954245A1 (en) * | 2017-09-11 | 2022-02-16 | Purple Innovation, LLC | Cushions comprising elastomeric material |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CH685003A5 (en) * | 1992-08-11 | 1995-02-28 | Buehler Ag | A method of continuously crystallizing and polymerizing plastic material, and apparatus therefor. |
| DE10331183B3 (en) * | 2003-07-04 | 2004-11-11 | Silverflex Gmbh Schwingungstechnik | - A vibration damping device consisting of upper and lower plates which are force locked together via an intermediate elastomer damping layer useful hydraulic impact road drills, flagstone compressors (sic), and vibratory sieves |
| JP4498833B2 (en) * | 2004-06-18 | 2010-07-07 | 株式会社ルートコーポレーション | Vibration absorber |
| ITBS20070005A1 (en) * | 2007-01-16 | 2008-07-17 | G & G Srl | ANTIVIBRATION ELEMENT, SHOCK ABSORBER AND SOUND RESISTANT |
| FR2924480B1 (en) * | 2007-12-04 | 2012-09-28 | Valeo Systemes Thermiques | VIBRATION DAMPER ELEMENT WITH IMPROVED PROFILE AND DEVICE EQUIPPED WITH SUCH A SHOCK ABSORBER |
| DE102010033028B4 (en) | 2010-08-02 | 2014-02-27 | Grammer Aktiengesellschaft | Vehicle vibration device with a horizontal suspension device |
| DE102010033419A1 (en) * | 2010-08-04 | 2012-02-09 | Grammer Aktiengesellschaft | Horizon spring device for vehicle seats with elastomer spring element with progressive spring characteristic |
| DE102010051326A1 (en) | 2010-08-31 | 2012-03-01 | Grammer Aktiengesellschaft | Vehicle seat for vehicles |
| DE102010052619A1 (en) | 2010-11-29 | 2012-05-31 | Grammer Aktiengesellschaft | Vehicle seat with guided scissor arms |
| DE102010053752A1 (en) | 2010-12-08 | 2012-06-14 | Grammer Aktiengesellschaft | Vehicle vibration device for vehicle seats or vehicle cabins |
| DE102010054749B4 (en) | 2010-12-15 | 2013-10-24 | Grammer Aktiengesellschaft | Suspension device for vehicle seats and / or vehicle cabins with elastomeric element |
| DE102011053647B4 (en) | 2011-09-15 | 2022-02-03 | Grammer Aktiengesellschaft | Vehicle seat with a suspension device and motor vehicle |
| DE102015113176B4 (en) | 2015-08-10 | 2021-12-30 | Grammer Aktiengesellschaft | Horizontal vibration device for a vehicle seat |
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| US2214942A (en) * | 1938-01-07 | 1940-09-17 | Gen Motors Corp | Flexible mounting for reciprocating engines |
| DE6913179U (en) * | 1969-04-01 | 1969-08-28 | Reisholz Stahl & Roehrenwerk | VIBRATING ELEMENT |
| EP0187888B1 (en) * | 1985-01-18 | 1987-12-09 | WOCO Franz-Josef Wolf & Co. | Spring body and process for its production |
| DE3607051A1 (en) * | 1986-03-04 | 1987-09-10 | Wolf Woco & Co Franz J | Resonance-damped spring |
| DE8717817U1 (en) * | 1987-11-23 | 1990-04-26 | Woco Franz-Josef Wolf & Co, 6483 Bad Soden-Salmuenster, De | |
| DE3803909A1 (en) * | 1988-02-09 | 1989-08-17 | Wolf Woco & Co Franz J | SPRING ELEMENT |
| US5229573A (en) * | 1991-10-15 | 1993-07-20 | Videojet Systems International, Inc. | Print quality laser marker apparatus |
-
1989
- 1989-01-23 DE DE3901898A patent/DE3901898A1/en not_active Withdrawn
- 1989-12-12 DE DE8989122918T patent/DE58903737D1/en not_active Expired - Fee Related
- 1989-12-12 ES ES198989122918T patent/ES2039820T3/en not_active Expired - Lifetime
- 1989-12-12 EP EP89122918A patent/EP0379689B1/en not_active Expired - Lifetime
-
1990
- 1990-01-10 MX MX019069A patent/MX172663B/en unknown
- 1990-01-23 JP JP2013470A patent/JPH02229927A/en active Pending
- 1990-01-23 CA CA002008354A patent/CA2008354A1/en not_active Abandoned
- 1990-01-23 BR BR909000250A patent/BR9000250A/en unknown
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3954245A1 (en) * | 2017-09-11 | 2022-02-16 | Purple Innovation, LLC | Cushions comprising elastomeric material |
| CN111872015A (en) * | 2020-06-01 | 2020-11-03 | 许昌学院 | Magnetic pulse mineralized refuse treatment device |
Also Published As
| Publication number | Publication date |
|---|---|
| MX172663B (en) | 1994-01-06 |
| ES2039820T3 (en) | 1993-10-01 |
| BR9000250A (en) | 1990-11-20 |
| EP0379689A1 (en) | 1990-08-01 |
| DE58903737D1 (en) | 1993-04-15 |
| JPH02229927A (en) | 1990-09-12 |
| DE3901898A1 (en) | 1990-07-26 |
| EP0379689B1 (en) | 1993-03-10 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| FZDE | Dead |