CA1140193A - Orbiting mass oscillator with oil film cushioned bearings - Google Patents
Orbiting mass oscillator with oil film cushioned bearingsInfo
- Publication number
- CA1140193A CA1140193A CA000362538A CA362538A CA1140193A CA 1140193 A CA1140193 A CA 1140193A CA 000362538 A CA000362538 A CA 000362538A CA 362538 A CA362538 A CA 362538A CA 1140193 A CA1140193 A CA 1140193A
- Authority
- CA
- Canada
- Prior art keywords
- rotor
- housing
- oscillator
- fluid
- mass
- 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.)
- Expired
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Abstract
Abstract of the Disclosure An orbiting mass oscillator has a rotor member orbitally driven in a housing and having an unbalanced mass. Damping means, for example, an oil cushion is provided between the oscillator rotor and opposing housing surfaces to absorb any sharp jolting forces developed and thereby alleviate damage to the rotor and the housing. The leading edge of the rotor adjacent the housing is inwardly curved providing funnelling means between the rotor and the housing to facilitate the maintenance of the oil cushion between the rotor and the housing when the rotor rotates.
Description
#1408 1 11~1~193 1 ¦ ORBITING MASS_ OSCILLATOR ~^~ITH OIL FIL,~'I CUSHI NED BEARINGS
2 I .,
3 ¦ S P E_C I_F I C A T I O N
4 ¦ This invention relates to orbiting mass oscillators, and
5 ¦ more particularly to such a device in which an effective oil cush-61 ion is formed between the rotor and housing of the oscillator.
71 In my Patent No 2,960,314, issued November 15, 1960, various 81 types of oscillators of the mechanical orbiting mass type are 9¦ described. In this type of oscillator, a rotor member is orbital-10¦ ly driven around in a housing, this rotor member having an unbal-11¦ anced mass such that sonic vibratory energy is generated thereby.
12 ¦ As described in my Patent No. 3,367,716, issued February 6, 1966, 13 ¦ this type of oscillator can be used quite effectively for cutting 14 ¦ rock by a type of operation wherein unidirectional pulses are 15 ¦ delivered to the cutter through a resonant vibration system, this 16 ¦ end result being achieved by means of an acoustic rectifier. This 17 ¦ type of rectifier operation often develops sharp jolting forces 18 ¦ which are transferred through the resonant vibration system back 19 ¦ to the oscillator which can result in sharp metal-to-metal con-20 ¦ tact between the rotor and the housing of the oscillator and cause 21 ¦ serious damage to these components. This problem is encountered 22 ¦ not only in earth and rock cutting operations, but also in sonic 231 energy systems of the type described wherein the resonantly vibrat-241 ing system involves the use of a transducer which feeds the vibra-251 tory energy into a liquid, such as described in my Patent No.
26¦ 3,740,028 to a non-resonant system, issued June 19, 1973. In 271 this non-resonant type of system, when the nower level reaches a 28¦ level such that cavitation bubbles are forméd, very high momentary 291 peak pressures are developed when the bubles collapse, these short 19.~
duration high level impulses being transferred back into the oscil-lator with the same undesirable results as mentioned above.
The oscillator of the present invention overcomes the aforementioned shortcomings of the prior art by providing an effective oil cushion or dampener between the oscillator rotor and the opposing oscillator housing surfaces. This cushioning effect is enhanced by rounding the leading edges of the rotor inwardly so as to facilitate the initial passage of the oil between the rotor and the housing as the rotor rotates. A relatively thick film of oil is provided and the possibilities of this film being "wiped away" with the relative movement between the bearing surfaces is minimized by providing the aforementioned turned-in leading edge on the rotor in the nature of a "ski-nose" which enables the rotor to effectively ride up onto the layer of oil.
It is therefore an object of this invention to minimize the damaging effects that sharp jolting pulses developed in a load might have on the bearing surfaces of an orbiting mass oscillator.
It is a further object of this invention to provide an improved orbiting mass oscillator having an oil film cushion which is formed and maintained between its bearing surfaces, thereby minimizing wear at these surfaces particularly in the face of sharp jolting drive pulses.
In accordance with the present invention there is provided in an orbiting mass oscillator having an unbalanced arcuate rotor which is orbitally driven around a cylindrical housing for generating vibratory energy for delivery to a load wherein sharp jolting forces are develoPed, the improvement being means for providinq cushioning between the rotor and the housing to dampen said forces comprising:
a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor having a curving ~"
114~1~3 leading edge providing a wedge effect such that the rotor rides upon said fluid which forms a thick cushioninq layer between the rotor and the housing, said rotor having a hollowed central portion and being in the form of first and second half cylinders, said first half cylinder forming an unbalanced rotor mass, said second half cylinder comprising a hollowed shell portion located in opposite relationship to the first half cylinder, there being a greater clearance space between the outer wall of said second half cylinder and the inner wall of the housing than between the outer wall of the first half cylinder and the inner wall of the housing, and means for flowing said fluid around said bearing surfaces.
Also in accordance with the invention there is provided in an orbiting mass oscillator for generating vibratory energy for delivery to a load wherein sharp jolting forces are developed, said oscillator having an unbalanced cylindrical rotor which is orbitally driven rotationally on a journal bearing within a cylindrical housing, the improvement being for providing cushion-ing between the rotor and the housing to dampen said forces comprising: a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor including a first "loaded" portion having a substantial radially unbalanced distri-bution of mass and a second "unloaded" portion having a substant-ially lower mass than said first portion, there being a larger radial gap clearance between the unloaded portion of the rotor and the housing than between the loaded portion of the rotor and the housing and a curving leading edge on said rotor between said loaded and unloaded portion forming a fluid wedge tapering toward said loaded portion such that the loaded portion of the rotor rides up onto said fluid which forms a thick cushioning - 2a~ -1~L4~1~3 layer between the rotor and the housing, and means for flowing said fluld into and around said bearing surfaces.
Other objects of this invention will become apparent as the description proceeds in connection with the accompanying drawings, of which:
FIGURE 1 is a cross-sectional view of a first embodiment of the invention;
FIGURE 2 is a cross-sectional view taken along the plane indicated by 2-2 in Figure l;
- 2b -~, 11~193 1 FIG 3 is an end view taken along the plan indicated by 3-3 2 in FIG l;
3 FIG 4 is an elevational view in cross section of the rotor of 4 the first embodiment;
FIG 5 is a view taken along the plane indicated by 5-5 in
71 In my Patent No 2,960,314, issued November 15, 1960, various 81 types of oscillators of the mechanical orbiting mass type are 9¦ described. In this type of oscillator, a rotor member is orbital-10¦ ly driven around in a housing, this rotor member having an unbal-11¦ anced mass such that sonic vibratory energy is generated thereby.
12 ¦ As described in my Patent No. 3,367,716, issued February 6, 1966, 13 ¦ this type of oscillator can be used quite effectively for cutting 14 ¦ rock by a type of operation wherein unidirectional pulses are 15 ¦ delivered to the cutter through a resonant vibration system, this 16 ¦ end result being achieved by means of an acoustic rectifier. This 17 ¦ type of rectifier operation often develops sharp jolting forces 18 ¦ which are transferred through the resonant vibration system back 19 ¦ to the oscillator which can result in sharp metal-to-metal con-20 ¦ tact between the rotor and the housing of the oscillator and cause 21 ¦ serious damage to these components. This problem is encountered 22 ¦ not only in earth and rock cutting operations, but also in sonic 231 energy systems of the type described wherein the resonantly vibrat-241 ing system involves the use of a transducer which feeds the vibra-251 tory energy into a liquid, such as described in my Patent No.
26¦ 3,740,028 to a non-resonant system, issued June 19, 1973. In 271 this non-resonant type of system, when the nower level reaches a 28¦ level such that cavitation bubbles are forméd, very high momentary 291 peak pressures are developed when the bubles collapse, these short 19.~
duration high level impulses being transferred back into the oscil-lator with the same undesirable results as mentioned above.
The oscillator of the present invention overcomes the aforementioned shortcomings of the prior art by providing an effective oil cushion or dampener between the oscillator rotor and the opposing oscillator housing surfaces. This cushioning effect is enhanced by rounding the leading edges of the rotor inwardly so as to facilitate the initial passage of the oil between the rotor and the housing as the rotor rotates. A relatively thick film of oil is provided and the possibilities of this film being "wiped away" with the relative movement between the bearing surfaces is minimized by providing the aforementioned turned-in leading edge on the rotor in the nature of a "ski-nose" which enables the rotor to effectively ride up onto the layer of oil.
It is therefore an object of this invention to minimize the damaging effects that sharp jolting pulses developed in a load might have on the bearing surfaces of an orbiting mass oscillator.
It is a further object of this invention to provide an improved orbiting mass oscillator having an oil film cushion which is formed and maintained between its bearing surfaces, thereby minimizing wear at these surfaces particularly in the face of sharp jolting drive pulses.
In accordance with the present invention there is provided in an orbiting mass oscillator having an unbalanced arcuate rotor which is orbitally driven around a cylindrical housing for generating vibratory energy for delivery to a load wherein sharp jolting forces are develoPed, the improvement being means for providinq cushioning between the rotor and the housing to dampen said forces comprising:
a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor having a curving ~"
114~1~3 leading edge providing a wedge effect such that the rotor rides upon said fluid which forms a thick cushioninq layer between the rotor and the housing, said rotor having a hollowed central portion and being in the form of first and second half cylinders, said first half cylinder forming an unbalanced rotor mass, said second half cylinder comprising a hollowed shell portion located in opposite relationship to the first half cylinder, there being a greater clearance space between the outer wall of said second half cylinder and the inner wall of the housing than between the outer wall of the first half cylinder and the inner wall of the housing, and means for flowing said fluid around said bearing surfaces.
Also in accordance with the invention there is provided in an orbiting mass oscillator for generating vibratory energy for delivery to a load wherein sharp jolting forces are developed, said oscillator having an unbalanced cylindrical rotor which is orbitally driven rotationally on a journal bearing within a cylindrical housing, the improvement being for providing cushion-ing between the rotor and the housing to dampen said forces comprising: a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor including a first "loaded" portion having a substantial radially unbalanced distri-bution of mass and a second "unloaded" portion having a substant-ially lower mass than said first portion, there being a larger radial gap clearance between the unloaded portion of the rotor and the housing than between the loaded portion of the rotor and the housing and a curving leading edge on said rotor between said loaded and unloaded portion forming a fluid wedge tapering toward said loaded portion such that the loaded portion of the rotor rides up onto said fluid which forms a thick cushioning - 2a~ -1~L4~1~3 layer between the rotor and the housing, and means for flowing said fluld into and around said bearing surfaces.
Other objects of this invention will become apparent as the description proceeds in connection with the accompanying drawings, of which:
FIGURE 1 is a cross-sectional view of a first embodiment of the invention;
FIGURE 2 is a cross-sectional view taken along the plane indicated by 2-2 in Figure l;
- 2b -~, 11~193 1 FIG 3 is an end view taken along the plan indicated by 3-3 2 in FIG l;
3 FIG 4 is an elevational view in cross section of the rotor of 4 the first embodiment;
FIG 5 is a view taken along the plane indicated by 5-5 in
6 FIG 4;
7 FIG 6 is a view taken along the plane indicated by 6-6 in
8 FIG 4;
9 FIG 7 is a top plan view in cross section of a second embodi-ment of the invention; and 11 ~IG 8 is a cross-sectional view taken along the plane indi-12 cated by 8-8 in FIG 7.
13 Referring now to FIGS 1-6, a first embodiment of the inven-14 tion is illustrated. Oscillator housing 11 has a rotor member 12 mounted therein, this rotor member being in the general form of 16 a crescent. The opposite ends of rotor 12 have end plates 13 and 17 14 which extend upwardly therefrom, plate 14 having an aperture 18 14a formed therein. Fixedly attached to end plate 13 is rotor 19 drive shaft 16 which is coupled to gear box 17 by means of a uni-versal joint 18. Oil is introduced into the housing through pipe 21 20, this oil preferably being a heavy lubrication oil, such as SAE
22¦ 10-30. The oil flows along the top surface 12a of the rotor and 231 passes from this surface through slots 19 formed through the 241 rotor at spaced intervals along its length to the bearing surface 25¦ 23 between the rotor and the inner wall of the housing.
26¦ The base portion lla of the housing is attached to a load 27 member which forms a resonant vibration system which may, for 28 example, comprise an elastic drill column 25 such as shown and 29 described in myLPatent No. 3,684,037, issued August 15, 1972. A
~ 93 1 prime mover, such as an electric motor, gasoline engine, etc.
2 (not shown), is coupled to gear box 17 and rotatably drives shaft 3 16 and along with it rotor 12 in an orbital path around the inner 4 wall of housing 11. Shaft 16 passes through end plate 14.
Rotor 12, as can best be seen in FIG 2, has an inwardly 6 curving leading edge portion 12b and a similarly inwardly curved 7 trailing edge portion 12c, these edges being in the general form 8 of a "ski-nose" such as to facilitate the passage of oil into the 9 space between the rotor and the housing wall as the rotor rotates.
In this manner, it is assured that the oil will not be wiped away 11 with such rotation, but rather will be forced into the space 12 between the rotor and the housing, thereby forming a thick cush-13 ioning film therebetween. Trailing edge 12c is made similar to 14 leading edge 12b so that if reverse rotation of the rotor is desired, the same effect will be achieved.
16 With operation of the device, the oil becomes packed between 17 the rotor and the housing to provide a cushion or dampener there-18 between. Thus, when the rotor is rotated at a speed such as to 19 cause resonant standing wave vibration of column 25, sharp vibra-tions on the column which may result when it strikes across hard 21 rock formations will be effectively cushioned at the interface 22 between the rotor and the housing so as to avoid damage to the 23 rotor or housing at such interface. As already noted, this type 24 of cushioning becomes particularly important where unidirectional "rectified" vibration pulses are being used to drive the cutter or 26 the like against hard material such as a rock formation and also 27 in non-resonant situations including where the load is a liquid 28 in which cavitation might occur. The end pieces 13 and 14 act 29 keep the rotor centered within the housing bore when it is 11~01~3 1 first started up. Circumferential grooves 26 are formed around 2 the inner wall of housing 11 to facilitate the circulation of 3 oil around the housing in lengthwise direction of the hore from groove to groove.
Referring now to FIGS 7 and 8, a second embodiment of the 6 invention is illustrated. This embodiment is the same as the 7 first except for the addition of a "basket" member which fits on 8 the top of the rotor in the form of an outer shell. Housing 11, 9 driveshaft 16 and gear box 17 are essentially as for the first embodiment. However, in the second embodiment a basket structure 11 30 is placed on the top of rotor 12 forming a top shell therefor.
12 Basket structure 30 is placed on or integrally formed with the 13 main portion of rotor 12 with the outer wall 30a of this structure 14 beins recessed inwardly of the main portion 12 of the rotor about 1/8" in a typical operative embodiment having a rotor diameter 16 of about 5". Thus, an approximately 1/8" space is provided be-17 tween the outer wall of basket member 30 and the inner wall of 18 the housing. As before, the leading and trailing edges 12b and 19 12c of the rotor are curved inwardly to facilitate the passage of the oil film between the rotor and the housing wall. Longi-21 tudinal oil flow from groove to groove is provided on the upper 22 wall of the housing through an oil inlet 40 which is coupled to 23 channel 41 formed in the housing, channel 41, in turn, being 24 coupled to longitudinal flow inducing circumferential groo~es 26 formed in the housing which circulate the oil lengthwise of the 26 annulus and around the entire rotor and shell portion. Excess oil 27 is permitted to flow out through oil outlet 27.
28 Thus, the oscillator of the present invention is provided 29 w h an effective oil film cushion or dampener at its rotation _ 5_ 114~1~3 1 interface with the housing wall, this cushion being efficiently 2 maintained by providing curved end leading edges for the rotor 3 which effectively channel the cushioning oil between the opposing 4 surfaces of these two members and avoids the oil being wiped away by this leading edge portion.
6 While the invention has been described and illustrated in 7 detail, it is to be clearly understood that this is intended by 8 way of illustration and example only and is not to be taken by way 9 of limitation, the spirit and scope of this invention being limited 11 on by the terms o the following claims.
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13 Referring now to FIGS 1-6, a first embodiment of the inven-14 tion is illustrated. Oscillator housing 11 has a rotor member 12 mounted therein, this rotor member being in the general form of 16 a crescent. The opposite ends of rotor 12 have end plates 13 and 17 14 which extend upwardly therefrom, plate 14 having an aperture 18 14a formed therein. Fixedly attached to end plate 13 is rotor 19 drive shaft 16 which is coupled to gear box 17 by means of a uni-versal joint 18. Oil is introduced into the housing through pipe 21 20, this oil preferably being a heavy lubrication oil, such as SAE
22¦ 10-30. The oil flows along the top surface 12a of the rotor and 231 passes from this surface through slots 19 formed through the 241 rotor at spaced intervals along its length to the bearing surface 25¦ 23 between the rotor and the inner wall of the housing.
26¦ The base portion lla of the housing is attached to a load 27 member which forms a resonant vibration system which may, for 28 example, comprise an elastic drill column 25 such as shown and 29 described in myLPatent No. 3,684,037, issued August 15, 1972. A
~ 93 1 prime mover, such as an electric motor, gasoline engine, etc.
2 (not shown), is coupled to gear box 17 and rotatably drives shaft 3 16 and along with it rotor 12 in an orbital path around the inner 4 wall of housing 11. Shaft 16 passes through end plate 14.
Rotor 12, as can best be seen in FIG 2, has an inwardly 6 curving leading edge portion 12b and a similarly inwardly curved 7 trailing edge portion 12c, these edges being in the general form 8 of a "ski-nose" such as to facilitate the passage of oil into the 9 space between the rotor and the housing wall as the rotor rotates.
In this manner, it is assured that the oil will not be wiped away 11 with such rotation, but rather will be forced into the space 12 between the rotor and the housing, thereby forming a thick cush-13 ioning film therebetween. Trailing edge 12c is made similar to 14 leading edge 12b so that if reverse rotation of the rotor is desired, the same effect will be achieved.
16 With operation of the device, the oil becomes packed between 17 the rotor and the housing to provide a cushion or dampener there-18 between. Thus, when the rotor is rotated at a speed such as to 19 cause resonant standing wave vibration of column 25, sharp vibra-tions on the column which may result when it strikes across hard 21 rock formations will be effectively cushioned at the interface 22 between the rotor and the housing so as to avoid damage to the 23 rotor or housing at such interface. As already noted, this type 24 of cushioning becomes particularly important where unidirectional "rectified" vibration pulses are being used to drive the cutter or 26 the like against hard material such as a rock formation and also 27 in non-resonant situations including where the load is a liquid 28 in which cavitation might occur. The end pieces 13 and 14 act 29 keep the rotor centered within the housing bore when it is 11~01~3 1 first started up. Circumferential grooves 26 are formed around 2 the inner wall of housing 11 to facilitate the circulation of 3 oil around the housing in lengthwise direction of the hore from groove to groove.
Referring now to FIGS 7 and 8, a second embodiment of the 6 invention is illustrated. This embodiment is the same as the 7 first except for the addition of a "basket" member which fits on 8 the top of the rotor in the form of an outer shell. Housing 11, 9 driveshaft 16 and gear box 17 are essentially as for the first embodiment. However, in the second embodiment a basket structure 11 30 is placed on the top of rotor 12 forming a top shell therefor.
12 Basket structure 30 is placed on or integrally formed with the 13 main portion of rotor 12 with the outer wall 30a of this structure 14 beins recessed inwardly of the main portion 12 of the rotor about 1/8" in a typical operative embodiment having a rotor diameter 16 of about 5". Thus, an approximately 1/8" space is provided be-17 tween the outer wall of basket member 30 and the inner wall of 18 the housing. As before, the leading and trailing edges 12b and 19 12c of the rotor are curved inwardly to facilitate the passage of the oil film between the rotor and the housing wall. Longi-21 tudinal oil flow from groove to groove is provided on the upper 22 wall of the housing through an oil inlet 40 which is coupled to 23 channel 41 formed in the housing, channel 41, in turn, being 24 coupled to longitudinal flow inducing circumferential groo~es 26 formed in the housing which circulate the oil lengthwise of the 26 annulus and around the entire rotor and shell portion. Excess oil 27 is permitted to flow out through oil outlet 27.
28 Thus, the oscillator of the present invention is provided 29 w h an effective oil film cushion or dampener at its rotation _ 5_ 114~1~3 1 interface with the housing wall, this cushion being efficiently 2 maintained by providing curved end leading edges for the rotor 3 which effectively channel the cushioning oil between the opposing 4 surfaces of these two members and avoids the oil being wiped away by this leading edge portion.
6 While the invention has been described and illustrated in 7 detail, it is to be clearly understood that this is intended by 8 way of illustration and example only and is not to be taken by way 9 of limitation, the spirit and scope of this invention being limited 11 on by the terms o the following claims.
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Claims
The embodiments of the invention in which an exclusive property or privilege is claimed are defined as follows:
In an orbiting mass oscillator having an unbalanced arcuate rotor which is orbitally driven around a cylindrical housing for generating vibratory energy for delivery to a load wherein sharp jolting forces are developed, the improvement being means for providing cushioning between the rotor and the housing to dampen said forces comprising:
a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor having a curving leading edge providing a wedge effect such that the rotor rides upon said fluid which forms a thick cushioning layer between the rotor and the housing, said rotor having a hollowed central portion and being in the form of first and second half cylinders, said first half cylin-der forming an unbalanced rotor mass, said second half cylinder com-prising a hollowed shell portion located in opposite relationship to the first half cylinder, there being a greater clearance space be-tween the outer wall of said second half cylinder and the inner wall of the housing than between the outer wall of the first half cylin-der and the inner wall of the housing, and means for flowing said fluid around said bearing surfaces.
The oscillator of Claim 1 and additionally including first and second end plates extending substantially normally to the longitu-dinai axis of said rotor and a drive shaft for said rotor which passes through one of said end plates.
In an orbiting mass oscillator for generating vibratory energy for delivery to a load wherein sharp jolting forces are developed, said oscillator having an unbalanced cylindrical rotor which is orbitally driven rotationally on a journal bearing within a cylindrical housing, the improvement being for providing cushion-ing between the rotor and the housing to dampen said forces com-prising:
a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor including a first "loaded" portion having a substantial radially unbalanced distribu-tion of mass and a second "unloaded" portion having a substantially lower mass than said first portion, there being a larger radial gap clearance between the unloaded portion of the rotor and the housing than between the loaded portion of the rotor and the housing and a curving leading edge on said rotor between said loaded and unloaded portion forming a fluid wedge tapering toward said loaded portion such that the loaded portion of the rotor rides up onto said fluid which forms a thick cushioning layer betweeen the rotor and the housing, and means for flowing said fluid into and around said bearing surfaces.
The oscillator of Claim 3 and additionally including first and second end plates extending substantially normally to the longitudinal axis of said rotor and a drive shaft for said rotor which passes through one of said end plates.
In an orbiting mass oscillator having an unbalanced arcuate rotor which is orbitally driven around a cylindrical housing for generating vibratory energy for delivery to a load wherein sharp jolting forces are developed, the improvement being means for providing cushioning between the rotor and the housing to dampen said forces comprising:
a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor having a curving leading edge providing a wedge effect such that the rotor rides upon said fluid which forms a thick cushioning layer between the rotor and the housing, said rotor having a hollowed central portion and being in the form of first and second half cylinders, said first half cylin-der forming an unbalanced rotor mass, said second half cylinder com-prising a hollowed shell portion located in opposite relationship to the first half cylinder, there being a greater clearance space be-tween the outer wall of said second half cylinder and the inner wall of the housing than between the outer wall of the first half cylin-der and the inner wall of the housing, and means for flowing said fluid around said bearing surfaces.
The oscillator of Claim 1 and additionally including first and second end plates extending substantially normally to the longitu-dinai axis of said rotor and a drive shaft for said rotor which passes through one of said end plates.
In an orbiting mass oscillator for generating vibratory energy for delivery to a load wherein sharp jolting forces are developed, said oscillator having an unbalanced cylindrical rotor which is orbitally driven rotationally on a journal bearing within a cylindrical housing, the improvement being for providing cushion-ing between the rotor and the housing to dampen said forces com-prising:
a supply of lubricating fluid to the bearing surfaces between the rotor and the housing, said rotor including a first "loaded" portion having a substantial radially unbalanced distribu-tion of mass and a second "unloaded" portion having a substantially lower mass than said first portion, there being a larger radial gap clearance between the unloaded portion of the rotor and the housing than between the loaded portion of the rotor and the housing and a curving leading edge on said rotor between said loaded and unloaded portion forming a fluid wedge tapering toward said loaded portion such that the loaded portion of the rotor rides up onto said fluid which forms a thick cushioning layer betweeen the rotor and the housing, and means for flowing said fluid into and around said bearing surfaces.
The oscillator of Claim 3 and additionally including first and second end plates extending substantially normally to the longitudinal axis of said rotor and a drive shaft for said rotor which passes through one of said end plates.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000362538A CA1140193A (en) | 1980-10-16 | 1980-10-16 | Orbiting mass oscillator with oil film cushioned bearings |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000362538A CA1140193A (en) | 1980-10-16 | 1980-10-16 | Orbiting mass oscillator with oil film cushioned bearings |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1140193A true CA1140193A (en) | 1983-01-25 |
Family
ID=4118167
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000362538A Expired CA1140193A (en) | 1980-10-16 | 1980-10-16 | Orbiting mass oscillator with oil film cushioned bearings |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1140193A (en) |
-
1980
- 1980-10-16 CA CA000362538A patent/CA1140193A/en not_active Expired
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|---|---|---|---|
| MKEX | Expiry |