EP1222368A1 - Anti-backlash sprag - Google Patents
Anti-backlash spragInfo
- Publication number
- EP1222368A1 EP1222368A1 EP99956621A EP99956621A EP1222368A1 EP 1222368 A1 EP1222368 A1 EP 1222368A1 EP 99956621 A EP99956621 A EP 99956621A EP 99956621 A EP99956621 A EP 99956621A EP 1222368 A1 EP1222368 A1 EP 1222368A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- drive
- piston
- fluid
- assembly
- 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.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/04—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft
- F01B9/08—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with rotary main shaft other than crankshaft with ratchet and pawl
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
- F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
- F01B9/026—Rigid connections between piston and rod; Oscillating pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
- F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
- F01L7/021—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with one rotary valve
- F01L7/022—Cylindrical valves having one recess communicating successively with aligned inlet and exhaust ports
Definitions
- the invention relates in general to a drive shaft assembly and, more particularly, to a drive shaft assembly which prevents backlash and reverse rotation of the drive shaft.
- crankshaft In the prior art, it is known to mechanically couple a piston to rotate a drive shaft.
- a crankshaft is used to transfer linear motion of the piston to rotational motion of the crankshaft.
- the operation of a crankshaft requires that a plurality of pistons be coupled to a single crankshaft to completely rotate the crankshaft.
- the present invention is a drive shaft assembly having a housing, a drive shaft and an overrunning clutch assembly.
- the overrunning clutch assembly has an inner race having an outer annular contact surface and an outer race having an inner annular contact surface.
- the inner annular contact surface and the outer annular contact surface form an annular space therebetween.
- the overrunning clutch assembly also has a plurality of sprags provided in the annular space, wherein the plurality of sprags allow the inner race to rotate in a first direction relative to the outer race, while preventing the inner race from rotating in a second direction relative to the outer race.
- the overrunning clutch assembly also is provided with means for maintaining the plurality of sprags in the annular space.
- the housing is secured to the outer race and the drive shaft is secured to the inner race.
- a piston and swing arm assembly is secured to the drive shaft to rotate the drive shaft in a first direction.
- the overrunning clutch secured to the housing prevents reverse rotation of the drive shaft to assure that the drive shaft is driven in only a single direction.
- Fig. 1 is a side elevation in cross-section showing the valve assembly and piston assembly of the present invention
- Fig. 2 is a perspective view of the valve assembly and piston assembly of Fig. 1;
- Fig. 3 is an exploded view of the valve assembly and piston assembly of Fig. 2;
- Fig. 4 is a top view in cross-section showing the arms and shaft assembly of Fig. 1;
- Fig. 5 is an exploded view in partial cut-away of the overrunning clutch assembly of the present invention.
- variable stroke motor is indicated generally as 10 in Fig. 1.
- the variable stroke motor includes a valve housing 12.
- the valve housing 12 is constructed of aluminum and provided with a hollow cylinder 14 to accommodate a valve shaft 16.
- the valve housing 12 is constructed to form a first fluid input 18 in fluid communication with the hollow cylinder 14 and a first fluid output 20 which is also in fluid commumcation with the hollow cylinder 14.
- the valve housing 12 is also formed with a second fluid input 22 and a second fluid output 24.
- the valve shaft 16 is provided with a first slot 26 and a second slot 28.
- the valve shaft 16 is also provided with a first ring seat 30, a second ring seat 32, and a third ring seat 34.
- Provided on the first ring seat 30, second ring seat 32, and third ring seat 34 are three Teflon rings 36, 38 and 40 which prevent the escape of fluid between the valve shaft 16 and hollow cylinder 14.
- a shaft rotator 42 which is operably secured to the key 44 extending from the valve shaft 16 shown in Fig. 3.
- the shaft rotator 42 may be a small electric motor or any similar rotation device known in the art.
- the first slot 26 and second slot 28 of the valve shaft 16 are disposed on opposite sides of the valve shaft 16. Accordingly, when the valve shaft 16 is positioned within the hollow cylinder 14 of the valve housing 12, as shown in Fig. 1, the second slot 28 opens fluid communication between the second fluid input 22 and the second fluid output 24. When the second slot 28 opens fluid communication between the second fluid input 22 and second fluid output 24, as shown in Fig. 1 , the first slot 26 is completely covered by the valve housing 12 (Figs. 1 and 3). The portion of the valve shaft 16 on the opposite side of the first slot 26, therefore, seals off fluid communication between the first fluid input 18 and first fluid output 20.
- the first slot 26 opens fluid communication between the first fluid input 18 and first fluid output 20, while the portion of the valve shaft 16 opposite the second slot 28 seals off fluid communication between the second fluid input 22 and second fluid output 28.
- the slots 26 and 28 and the inputs 18 and 22 and the outputs 20 and 24 are sized so that when the fluid communication between the first fluid input 18 and first fluid output 20 is open, fluid communication between the second fluid input 22 and second fluid output 24 is closed. Similarly, when fluid communication between the second fluid input 22 and second fluid output 24 is open, fluid communication between the first fluid input 18 and first fluid output 20 is closed.
- a drive housing 46 Secured to the valve housing 12 is a drive housing 46 which forms a drive cylinder 48 as shown in Fig. 1.
- the drive housing 46 is constructed of stainless steel seamless tubing.
- the drive housing 46 is secured to a drive box 50 which, is preferably constructed of aluminum.
- a piston 52 Provided within the drive cylinder 48 is a piston 52.
- the piston 52 is preferably constructed with an aluminum cap 54 and an aluminum base 56.
- the piston 52 is provided with a plastic sealing ring 58 which allows the piston 52 to pivot two degrees from a position normal to the center axis of the drive cylinder 48, while
- a piston rod 60 preferably constructed of hardened steel is secured to the piston 52 with a securement screw 61 (Fig. 1). As shown in Fig. 3, the piston rod 60 is provided with an eyelet 62 which fits within a yoke 64 of a swing arm 66. Provided within the eyelet 62 is a needle roller bearing 68 or similar bearing known in the art to reduce friction. The needle roller bearing 68 is positioned within the eyelet 62, the eyelet 62 positioned within the yoke 64 and a dowel pin 70 constructed of heat treated steel is positioned through a first eyelet 72 of the yoke 64, the needle roller bearing 68, and a second eyelet 74 of the yoke 64.
- the dowel pin is preferably constructed of heat treated steel to withstand the large pressures associated with actuation of the piston rod 60.
- the swing arm 66 is preferably constructed of hardened steel and is provided with a large hole 76 to accommodate a pair of drive sprags 78.
- the drive sprags 78 are coupled to a drive shaft 80 in a manner which transfers rotational energy from the swing arm 66 to the drive shaft 80 on the drive stroke and which allows the drive shaft 80 to "freewheel" relative to the swing arm 66 on the recovery stroke so that the drive shaft 80 is not rotated in the opposite direction.
- the drive shaft 80 extends through the drive box 50 to power a vehicle or any other drivable device.
- a fluid pressure generator 82 Operably coupled in fluid communication with the first fluid input 18, is a fluid pressure generator 82 (Fig. 2).
- the pressure generator 82 is a steam generator, but the pressure generator 82 may, of course, be any similar device.
- the fluid pressure generator 82 is coupled to the first fluid input 18 via a transfer hose 84 (Figs. 2 and 3).
- the second fluid output 24 is also coupled to the fluid pressure generator 82 by a supplemental transfer hose 86.
- variable stroke motor 10 is also provided with a supplemental valve and piston assembly 88.
- the supplemental valve and piston assembly 88 is substantially similar in design to the assembly described above.
- the valve shaft 16 is provided with a third slot 90 and a fourth slot 92 positioned on the valve shaft 16 in reverse of the positions of the first slot 26 and second slot 28.
- This positioning of the slots 26, 28, 90 and 92 causes the piston 52, described above, to drive when the piston 94 of the supplemental valve and piston assembly 88 is recovering, and to recover when the piston 94 of the supplemental valve and piston assembly 88 is driving.
- This complimentary actuation of the pistons 52 and 94 causes the drive shaft 80 to be substantially continuously driven by one of the two pistons 52 and 94.
- two recovery springs 96 and 98 are provided to return the swing arm 66, described above, and the swing arm 100 of the supplemental valve and piston assembly 88 to a starting position. As each swing arm 66 and 100 alternately moves to a starting position, the swing arms 66 and 100 move their respective pistons 52 and 94 to a starting position as well.
- the recovery springs 96 and 98 are secured to the drive box 50 around the drive shaft 80.
- Each recovery spring 96 and 98 is provided with a recovery arm 102 and 104 and a securement finger 106 and 108. Once the recovery springs 96 and 98 are secured to the drive box 50, the fingers 106 and 108 are positioned within holes 110 and 112 provided in the swing arms 66 and 100.
- the drive shaft 80 is coupled to the interior perimeters of a pair of drive sprags 114 which, in turn, are coupled on their exterior perimeters to the swing arm 100.
- the drive sprags 114 are oriented so that as the swing arm 100 is driven by the piston 94, the drive sprags 114 transfer the rotational motion of the swing arm 100 to the drive shaft 80.
- the drive sprags 1 14 "freewheel" to allow the recovery spring 96 to return the swing arm 100 to its starting position without transferring a large amount of rotational energy to the drive shaft 80.
- An anti-backlash sprag 116 is secured to the drive shaft 80 between the swing arms 66 and 100 to further reduce the transfer of rotational energy between the swing arms 66 and 100 and the drive shaft 80.
- the anti -backlash sprag 116 is secured to the drive box 50 within a drive shaft opening 118 provided in the drive box 50 between the swing arms 66 and 100.
- the anti -backlash sprag 116 is secured to the drive box 50 by weldments or other similar securement means.
- the anti-backlash sprag 116 is similar in construction to the drive sprags 114, but is coupled to the drive shaft 80 in an opposite operational orientation relative to the drive sprags 114.
- the drive sprags 114 transfer rotational energy of the swing arm 100 to the drive shaft 80.
- the anti-backlash sprag 116 is in its "freewheel” orientation, allowing the drive shaft 80 to rotate freely.
- the recovery spring 96 returns the swing arm 100 to its starting position.
- the drive sprags 114 are in their "freewheel” orientation which limits rotational energy transfer from the swing arm 100 to the drive shaft 80 and reduces the drag on the recovery spring 96.
- the anti-backlash sprag 116 is provided with an outer race 120 and an inner race 122. Both the outer race 120 and inner race 122 are preferably constructed of hardened steel to increase the longevity of the anti-backlash sprag 116.
- the outer race 120 is provided with inner annular contact surface 124.
- the outer race 120 is also provided with an exterior surface 126 which is welded or otherwise secured to the drive housing 50 as shown (Figs. 4 and 5).
- the inner race 122 may be provided with a keyed inner annular surface 128 for connection to the drive shaft 80 which may or may not be provided with a similar keyed surface (not shown) to facilitate transfer of torque from the drive shaft 80 to the inner race 122.
- the inner race 122 is also provided with an outer annular contact surface 130.
- the sprag assembly 132 comprises a sprag retainer 134, a pair of coil springs 136 and a plurality of sprags 138.
- the coil springs 136 bias the sprags 138 into an upright position.
- the sprags 138 are in their upright position, however, there is not sufficient distance between the outer race 120 and the inner race 122 to insert the sprag assembly 122 therebetween.
- the sprags 138 must be tilted slightly to allow assembly of the anti-backlash sprag 116.
- the sprags 138 are each preferably provided with a body 140 to contact the outer annular contact surface 130 of the inner race 122 and a head 142 to contact the inner annular contact surface 124 of the outer race 120.
- the bodies 140 are slightly wider and shorter than both the heads 142 and openings 144 provided in the sprag retainer 122.
- the width of the bodies 140 prevents the sprags 138 from falling out of the sprag retainer 134.
- the length of the bodies 140 provides sufficient clearance for placement of the coil springs 136 between the bodies 140 and sidewalls 146 of the sprag retainer 134. Because the bodies 140 are shorter than the heads 142, the coil springs 136 are able to bias an overhanging portion 148 of the heads 142 outward, thereby biasing the sprags 138 into their upright position.
- the sprag assembly 132 When the anti-backlash sprag 116 is fully assembled, the sprag assembly 132 is placed within the outer race 124, and the inner race 122 is placed within the sprag assembly 132 (Figs. 4 and 5).
- the inner race 122 is thereby allowed to rotate in a first direction (counterclockwise as shown) relative to the outer race 120, because this rotation tilts the sprags 138 away from their upright position.
- the anti-backlash sprag 116 prevents rotation of the inner race 122 in the opposite direction (clockwise as shown) relative to the outer race 120, as this rotation allows the sprags 138 to tilt toward their upright position, thereby wedging the sprags 138 between the inner race 14 and the outer race 120.
- the drive shaft 80 which is secured to the inner race 14, is free to rotate in a counterclockwise direction relative to the anti-backlash sprag 116 as such rotation tilts the sprags 138 away from their upright position.
- the coil springs 136 bias the sprags 138 toward their upright position, thereby transferring torsional forces of the inner race 122 to the outer race 120. Because the outer race 120 is welded to the drive box 50, rotation of the drive shaft 80 in a clockwise direction is prevented by the anti-backlash sprag 116.
- the anti-backlash sprag 116 is provided to prevent any further rotation of the drive shaft 80 in the direction of the swing arm 100 recovery. If the friction between the drive sprags 114 and drive shaft 80 is great enough to transfer some amount of rotational energy from the drive sprags 114 to the drive shaft 80 during the recovery stroke of the swing arm 100, the anti-backlash sprag 116 prevents rotation of the drive shaft 80. Since the anti-backlash sprag 116 is welded to the drive box 50, the anti-backlash sprag 116 transfers any "backward" rotational energy of the drive shaft 80 to the drive box 50 to prevent rotation of the drive shaft 80 in the direction of the swing arm 100 recovery.
- the anti-backlash sprag 116 continues to prevent backward rotation of the drive shaft 80 until one of the swing arms 66 or 100 begins rotating the drive shaft 80 on the drive stroke. In this way, the anti-backlash sprag 116, assures that the drive shaft 80 is rotated in only a single direction.
- the shaft rotator 42 is actuated to rotate the valve shaft 16 within the hollow cylinder 14.
- the fluid pressure generator 82 is then actuated to supply a pressurized fluid, such as steam, to the first fluid input 18 and to the supplemental valve and piston assembly 88.
- the valve shaft 16 is thereby being rotated at a constant speed.
- fluid is being applied at a low pressure to the first fluid input 18, only a small amount of fluid enters the drive cylinder 58 as the first slot 26 opens fluid communication between the first fluid input 18 and first fluid output 20. This introduction of fluid into the drive cylinder 48 forces the piston 52 away from the valve housing 12.
- the eyelet 62 of the piston rod 60 pivots slightly as the swing arm 66 reciprocates. This pivoting of the piston rod 60 causes the entire piston 52 to tilt slightly relative to the drive cylinder 48. To reduce the amount of tilt, the piston 52 is arranged so that in both its starting position and its ending position the piston 52 is slightly tilted. This reduces the degree of tilt of the piston 52 when the piston is at the center of a full stroke.
- the swing arm 66 and piston rod 60 are preferably designed with lengths sufficient to place the piston 52 in a starting position wherein the piston 52 is tilted two degrees from normal, relative to the center axis of the drive cylinder 48.
- the piston 52 continues to pivot away from the drive shaft 80 until the piston 52 is halfway through its full stroke as shown in Fig. 1. At this point, the piston 52 is two degrees from normal relative to the axis of the drive cylinder 48, but in a direction opposite the two-degree orientation of the starting point. As the drive cylinder 48 continues to fill with fluid, the swing arm 66 rotates further, until the piston 52 is three-quarters of the way through its full stroke. At this point the swing arm 66 has rotated sufficiently so that the piston 52 is again normal to the center axis of the drive cylinder 48.
- the piston 52 is oriented two degrees from normal to start. In this way the piston 52 starts at a position two degrees from normal, cycles through a normal position, a position two degrees from normal in the opposite direction, another normal position, and finally a position two degrees from normal in the same direction as the starting position. The total amount of deviation from the normal position is thereby kept to a minimum throughout the full stroke.
- variable stroke motor 10 is fully capable of cycling through the full stroke noted above, this full stroke is only realized under full fluid pressure.
- the piston 52 moves through a much shorter stroke cycle.
- the pressure of the fluid supplied by the fluid pressure generator 82 increases, a larger amount of fluid passes from the first fluid input 18, through the first fluid output 20 and into the drive cylinder 48 with each rotation of the valve shaft 16.
- This larger amount of fluid entering the drive cylinder 48 moves the piston 52 more quickly, thereby generating a longer and longer stroke.
- the swing arm 66 translates this longer stroke into a greater rotation of the drive shaft 80.
- each cycle takes the same amount of time, regardless of the pressure of the fluid being applied. Accordingly, a greater rotation of the drive shaft 80 in the same amount of time translates into a greater speed of the drive shaft 80.
- the second slot 28 provided on the valve shaft 16 opens fluid communication between the second fluid input 22 and second fluid output 24 one time (Fig. 1).
- the force of the recovery spring 96 causes the swing arm 66 to push the piston rod 60 into the piston 52, thereby pushing fluid out of the drive cylinder 48 through the second fluid input 22 and second fluid out 24.
- the fluid is thereafter returned to the fluid pressure generator 82 through the supplemental transfer hose 86, so that the fluid can again be pressurized and recirculated through the motor 10 (Fig. 2).
- the supplemental valve and piston assembly 88 is working in a reciprocating manner, to drive the drive shaft 80 when the piston 52 is in its recovery stroke.
- the anti-backlash sprag 116 prevents the swing arms 66 and 100 from transferring rotational energy to the drive shaft 80 during their recovery stroke.
- valve shaft 16 Since the valve shaft 16 is rotated at a constant speed, varying the amount of fluid pressure entering the first fluid input 18 causes the piston 52 to stroke a longer distance, and thereby drive the drive shaft 80 a greater distance during the same interval.
- the fluid pressure generator 82 may be provided with a heating adjustment control 150, such as a propane valve, to vary the amount of heat delivered to the fluid pressure generator 82 and, thereby, the pressure of the fluid. Accordingly, the variable stroke motor 10 can directly convert a larger amount of heat energy into a faster rotation of the drive shaft 80.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Hydraulic Motors (AREA)
- Transmission Devices (AREA)
Abstract
Description
Claims
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/US1999/024520 WO2001029378A1 (en) | 1999-10-19 | 1999-10-19 | Anti-backlash sprag |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1222368A1 true EP1222368A1 (en) | 2002-07-17 |
Family
ID=22273863
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99956621A Withdrawn EP1222368A1 (en) | 1999-10-19 | 1999-10-19 | Anti-backlash sprag |
Country Status (9)
Country | Link |
---|---|
EP (1) | EP1222368A1 (en) |
JP (1) | JP2003522314A (en) |
KR (1) | KR20020091048A (en) |
CN (1) | CN1378616A (en) |
AU (1) | AU1318800A (en) |
CA (1) | CA2388368A1 (en) |
MX (1) | MXPA02003911A (en) |
PL (1) | PL354953A1 (en) |
WO (1) | WO2001029378A1 (en) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN114198427B (en) * | 2021-10-20 | 2023-05-05 | 中国航发四川燃气涡轮研究院 | Control structure for controlling bidirectional controllable overrunning clutch |
CN114263711A (en) * | 2021-12-03 | 2022-04-01 | 周旭亮 | Rotary power transmission device and vehicle power assembly system |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR1308756A (en) * | 1961-09-30 | 1962-11-09 | Explosion motor with faster, more powerful thrusts and shaft speed variation by its assembly | |
US5152254A (en) * | 1991-10-31 | 1992-10-06 | Masami Sakita | Internal combustion engine for vehicles |
US5562075A (en) * | 1995-05-08 | 1996-10-08 | Walsh; Noel J. | Oscillating drive shaft and related components configuration for reciprocating piston engines |
US5967016A (en) * | 1997-02-14 | 1999-10-19 | Thermal Dynamics, Inc. | Anti-backlash sprag |
-
1999
- 1999-10-19 MX MXPA02003911A patent/MXPA02003911A/en unknown
- 1999-10-19 AU AU13188/00A patent/AU1318800A/en not_active Abandoned
- 1999-10-19 CA CA002388368A patent/CA2388368A1/en not_active Abandoned
- 1999-10-19 WO PCT/US1999/024520 patent/WO2001029378A1/en not_active Application Discontinuation
- 1999-10-19 CN CN99817011A patent/CN1378616A/en active Pending
- 1999-10-19 EP EP99956621A patent/EP1222368A1/en not_active Withdrawn
- 1999-10-19 PL PL99354953A patent/PL354953A1/en unknown
- 1999-10-19 JP JP2001532342A patent/JP2003522314A/en active Pending
- 1999-10-19 KR KR1020027005046A patent/KR20020091048A/en not_active Application Discontinuation
Non-Patent Citations (1)
Title |
---|
See references of WO0129378A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2001029378A1 (en) | 2001-04-26 |
AU1318800A (en) | 2001-04-30 |
CA2388368A1 (en) | 2001-04-26 |
PL354953A1 (en) | 2004-03-22 |
MXPA02003911A (en) | 2003-09-25 |
JP2003522314A (en) | 2003-07-22 |
KR20020091048A (en) | 2002-12-05 |
CN1378616A (en) | 2002-11-06 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20020425 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
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AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: THERMAL DYNAMICS, INC. |
|
RIN1 | Information on inventor provided before grant (corrected) |
Inventor name: SIMONDS, EDWARD |
|
17Q | First examination report despatched |
Effective date: 20041021 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN |
|
18D | Application deemed to be withdrawn |
Effective date: 20050301 |