GB2133837A - Rotary fluid-pump - Google Patents
Rotary fluid-pump Download PDFInfo
- Publication number
- GB2133837A GB2133837A GB08401214A GB8401214A GB2133837A GB 2133837 A GB2133837 A GB 2133837A GB 08401214 A GB08401214 A GB 08401214A GB 8401214 A GB8401214 A GB 8401214A GB 2133837 A GB2133837 A GB 2133837A
- Authority
- GB
- United Kingdom
- Prior art keywords
- cavity
- casing
- cam rotor
- fluid pump
- vanes
- 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- Withdrawn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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3566—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along more than line or surface
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/356—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C2/3566—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along more than one line or surface
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
The pump has a cylindrical cavity accommodating a symmetrically- shaped cam-rotor (36) with the lobe portions (36a, 36b) thereof slightly spaced from the cylindrical wall, (34a) of the cavity. Vanes (42, 44) are slidingly mounted in diametrically-opposed portions of the cylindrical wall (34a) and are biassed by e.g. springs (46a, 46b), towards the rotor. Two pairs of fluid inlet means (50a, 50b) and fluid outlet (52a, 52b) means are associated with the diametrically-opposed portions of the cylindrical wall (34a). The pump may be employed as a steam or vapour compressor in an I.C. engine cooling system, Fig. 1. <IMAGE>
Description
SPECIFICATION
Fluid pump
The present invention relates in general to a fluid pump, and more particularly to a compressor which, by way of example, finds utility in a closed circuit type engine cooling system which cools the engine by latent heat of evaporation of a coolant.
In the engine cooling system of the type as mentioned above, there is sometimes employed a compressor for compressing the vapor or steam generated in a coolant jacket of the engine before condensing it. Because the compressing efficiency of the compressor has direct effects upon the cooling efficiency of the cooling system many attempts have been hitherto carried out to improve the performance of the compressor.
However, as will become clear hereinafter, some of the existing compressors fail to have sufficient performance for practical use in such engine cooling system.
Hereinafter, the cooling system of the above-mentioned type will be referred to as a coolant evaporation latent heat-used engine cooling system or CELH-engine cooling system, in order to facilitate the description.
According to the present invention, there is provided a vane-type compressor which is particularly usable in the coolant evaporation latent heat-used engine cooling system (CELHengine cooling system).
According to the present invention, there is provided a fluid pump for pumping a fluid, which comprises a casing having a cylindrical cavity formed therein; a symmetrically shaped cam rotor rotatable in the cylindrical cavity about the axis thereof coincident with the axis of the cylindrical cavity, the cam rotor rotating in the cavity having the tops of the two lobe portions thereof slightly spaced from the cylindrical inner surface of the cavity; two vanes respectively and slidably received in two bores which are formed in diametrically opposed portions of the casing with respect to the axis of the cylindrical cavity, the bores being exposed to the cavity; biasing means for biasing the two vanes toward the cam rotor so that the leading ends of the two vanes are contstantly in contact with the outer surface of the cam rotor; and two pairs of inlet and outlet means which are associated with the diametrically opposed portions of the casing so that under rotation of the cam rotor, the fluid is introduced through the inlet into the cylindrical cavity and discharged therefrom into the outside through the outlet.
Objects and advantages of the present invention will become apparent from the following description when taken in conjunction with the accompanying drawings, in which:
Fig. 1 is an illustration of a CELH-engine cooling system to which a vane-type compressor of the present invention is applicable;
Fig. 2 is a laterally sectional view of a conventional rotary vane-type compressor;
Fig. 3 is a longitudinally sectional view of a compressor according to the present invention;
Fig. 4 is a laterally sectional view of the compressor of Fig. 3; Fig. 5 is a graph showing the characteristics of the vanes provided in the compressor of the present invention; and
Fig. 6 is an illustration depicting the vapor discharging ability of the compressor of the present invention.
Prior to describing the invention, the cooling evaporation latent heat-used engine cooling system (or CELH-engine cooling system) will be outlined with reference to Fig. 1 because the compressor of the present invention is particularly applicable to such cooling system. This system basically features an arrangement wherein the coolant in the coolant jacket defined in the engine proper 10 is permitted to boil and the gaseous and/or boiling coolant passes out through a check valve 12 to a compressor 14. The compressor compresses the gaseous coolant raising the temperature and pressure thereof and pumps the same into an air cooled heat exchanger 1 6 or condenser. Due to the high temperature differential between the atmosphere and the high temperature-pressure vapor, the cooling efficiency of this arrangement is remarkably high.
Subsequent to condensation in the heat exchanger 16, the coolant is recirculated back into the coolant jacket of the engine 10. The arrows shown in this drawing indicate the direction in which the coolant travels. The compressor 14 hereinshown is belt-driven by the engine 10 through two pulleys 18 and 20.
In order to clarify the invention, one conventional rotary vane-type compressor will be outlined with reference to Fig. 2.
Within a casing 22 having a cylindrical surface, there is disposed a cylindrical rotor 24 which rotates about its axis 02 offset from the axis O of the cylindrical inner surface of the casing 22. The rotor 24 rotates in the casing 22 establishing substantially a surface-to-surface contact between the cylindrical outer surface of the rotor 24 and the cylindrical inner surface of the casing 22. The rotor 24 is formed with a diametrically extending bore into which a pair of vanes 26 are slidably received. The vanes 26 are biased outwardly, that is in the opposed directions, by a spring 28 disposed therebetween, so that the leading ends of the vanes 26 are constantly in contact with the cylindrical inner surface of the casing.Thus, upon rotation of the rotor 24 in the direction of the arrow R, the two chambers A1 and
A2 are subjected to a voluminal change thereby causing a fluid or gas flow in the direction of the arrows B, that is in the direction from the inlet opening 30 to the outlet opening 32.
However, the above-mentioned conventional compressor has the following drawbacks.
First, the surface-to-surface contact between the rotor 24 and the casing 22 leads to relatively large frictional losses imparing the efficiency of the compressor. If, in order to solve the frictional losses, the rotor 24 is arranged to rotate having a slight clearance between it and the casing 22, the pumping or compressing efficiency of the compressor is greatly reduced.
Second, mounting the vanes 26 in the eccentrically arranged rotor 24 tends to produce undesirable vibration of the rotor. That is to say, the two vanes 26 are forced to move in different manners upon rotation of the rotor thereby causing unbalanced rotation of the rotor 24.
Third, the inherent construction wherein the rotation axis of the rotor 24 is offset from the axis of the casing 22 induces troublesome machining work in producing the compressor. Viz., it is impossible to reduce the clearance defined between the rotor 24 and the casing 22 to the desired limit, especially in view of the fact that such clearance should be made by taking into consideration the wear which occurs with the passing of time.
Fourth, due to its inherent construction, it is impossible to increase, to a sufficient level, the ecentricity of the rotor 24 relative to the casing 22. Thus, the fluid discharging capacity is small as compared with the entire construction of the compressor.
In order to solve the above-mentioned drawbacks encountered in the conventional rotary vane-type compressor, the present invention is proposed.
Referring to Figs. 3 and 4, there is shown a vane-type compressor according to the present invention.
In the embodiment within a casing 34 having a cylindrical inner surface 34a, there is rotatably disposed a symmetrically shaped cam rotor 36.
The rotor 36 rotates about its axis 0 coincident with the axis 0 of the cylindrical cavity 34a of the casing 34. As is understood from Fig. 4, the rotor 36 rotates in the casing 34 having the tops 36c and 36d of the diametrically opposed two lobe portions 36a and 36b thereof slightly spaced from the cylindrical inner surface 34a of the casing 34.
As will be apparent as the description proceeds, the top 36c or 36d of each lobe portion 36a or 36b has a curved surface concentric with the cylindrical inner surface 34a of the casing 34. The curved surface 36c or 36d defines an angle "" with respect to the axis 0 of the rotor 35, as shown. The casing 34 is formed at the diametrically opposed enlarged portions with respective rectangular bores 38 and 40 which are exposed to the cylindrical cavity 34a and are arranged symmetrical with respect to the axis 0.
Within each bore 38 or 40 is slidably received a rectangular vane 42 or 44. The vanes 42 and 44 are biased by springs 46a and 46b toward the cam rotor 36, so that the leading ends of the vanes 42 and 44 are constantly in contact with the outer surface 36e of the cam rotor 36 upon rotation of the rotor 36. As is seen from Fig. 3, the lateral sides of each vane 42 or 44 are slightly spaced from two side covers 48 and 50 which are bolted to the casing 34 to cover the open sides of the same. At each of the enlarged portions of the casing 34, there are formed an inlet passage 50a or 50b and an outlet passage 52a or 52b which are arranged to have therebetween the associated bore 38 or 40. Each outlet passage 52a or 52b is provided with a check valve 54a or 54b which is biased to close the passage by a spring 56a or 56b.The check valve 54a or 54b functions to shut out the back flow from the outside to the cavity 34a of the casing 34 but permit forward flow from the cavity 34a to the outside when the pressure in the cavity 34a is higher than a predetermined degree.
As is seen from Fig. 3, the cam rotor 36 has a shaft 58 integral therewith, which shaft is rotatably supported through bearings 60 by the side cover 50 which is secured to a suitable fixed member (not shown). Designated by numeral 62 is a seal for sealing the clearance between the side cover 50 and the shaft 58. A pulley 61 is secured to the shaft 58 by a bolt (no numeral) to rotate therewith about the axis thereof. The pulley 61 and thus the cam rotor 36 are driven by a suitable mover such as the engine per se through a belt (not shown) engaging the pulley 61.
In the following, operation will be described with reference to the drawing of Fig. 4 and the graph of Fig. 5 which shows at its lower section the relationship (the curve "b") between the angular position "0" of the cam rotor 36 and the axial displacement of each vane 42 or 44. For ease with which the following description is carried out, explanation will be commenced with respect to the condition wherein the cam rotor 36 assumes its vertical position as shown in Fig. 4, that is, the zero angular position of the graph of
Fig. 5.
When the cam rotor 36 rotates for 1 80 degrees from the vertical position, the leading end of each vane 42 or 44 is moved to describe the path of the curve "b" in Fig. 5. That is, when the cam rotor 36 assumes the vertical position, the leading end of each vane 42 or 44 contacts the diametrically smallest base portion "A" of the cam rotor 36. In this condition, each vane 42 or 44 is fully projected into the cavity 34a of the casing 34.
With rotation of the cam rotor 36 in the direction of the arrow "D", each vane 42 or 44 is moved outwardly against the force of the spring 46a or 46b while keeping contact with the cam surface 36e of the rotor 36. When the tops of the lobe portions 36a and 36b come into contact with the vanes 42 and 44, these vanes are fully depressed as is indicated by the top portion of the curve "b".
After this, the vanes 42 and 44 are gradually projected into the cavity 34a and assume their fully projected positions when the cam rotor 36 comes to the 1 80 degree angular position. Further rotation of the cam rotor 36 induces identical movements of the vanes 42 and 44 to the above-mentioned movement.
Fig. 5 shows at its upper section a curve "a" which describes the acceleration applied to each vane 42 or 44 during the rotation of the cam rotor 36 from the zero angular position to the 180 degree angular position. As is known to those skilled in the art, the acceleration is obtained by differentiating the displacement of the vane 42 or 44 twice by time. It is to be noted that the acceleration curve "a" obtained in the invention is flattened at each of its positive and negative acceleration zones. If the acceleration curve has any peak or suddenly projected point thereon, the vane 42 or 44 tends to jump and bound during its reciprocating axial movement, causing undesired vibration of the casing 36.Thus, shaping of the cam rotor 36 is effected by taking the above fact into consideration, that is, the shaping is so made as to flatten, the acceleration curve "a" as much as possible. As is seen from the middle portion of the curve "a", the acceleration of each vane 42 or 44 is zero when the top 36c or 36d of each lobe portion 36a or 36b engages the vane 42 or 44.
During the time for which the cam rotor 36 rotates for 1 80 degrees from its horizontal position as schematically shown in Fig. 6 (wherein each vane 42 or 44 is fully depressed and has zero acceleration), the four chambers (see Fig. 4) defined by the dylindrical inner surface 34a of the casing 34, the outer surface 36e of the cam rotor 36 and the inwardly projected portions of the vanes 42 and 44 are subjected to a voluminal change, viz., intake mode, compressing mode and discharge mode, at both sides of the cam rotor 36.
Thus, the gas contained in the hatched zones of
Fig. 6 is all pumped out as the cam rotor 36 rotates for 1 80 degrees. More particularly, the above-mentioned three modes which complete one pumping cycle are carried out twice per single rotation of the cam rotor 36. Thus, the compressor of the present invention works substantially twice as hard as the above-mentioned conventional compressor.
With the construction as mentioned hereinabove, the compressor according to the present invention is free of the drawbacks encountered in the conventional rotary vane type compressor. In fact, first, since the cam rotor 36 per se is not in contact with the cylindrical inner surface 34a of the casing 34, the efficiency drop of the compressor caused by the frictional losses does not occur. Second, since substantially all parts are forced to move in substantially the same manner upon rotation of the cam rotor 36, the undesirable vibration of the compressor is not produced. Third, since the parts and portions are constructed and arranged symmetrically with respect to the center of the compressor, production of the compressor by machining is greatiy facilitated. Fourth, since two pumping cycles are carried out per one rotation of the cam rotor 36, large fluid discharging capacity is expected and thus the compressor can be made compact.
If, furthermore, each of the springs 46a and 46b has a fine winding (small pitch) at the casing side and a rough winding (large pitch) at the vane side, undesirable surging phenomenon of the springs are suppressed. In this case, high speed rotation of the cam rotor 36 is more assuredly effected.
Although, the above description has been made with respect to the CELH-engine cooling system, it is a matter of course to apply the compressor of the invention to other field wherein fluid compression and/or fluid pumping is necessitated.
Claims (7)
1. A fluid pump for pumping a fluid, comprising:
a casing having a cylindrical cavity formed therein;
a symmetrically shaped cam rotor rotatable in said cylindrical cavity about the axis thereof coincident with the axis of said cylindrical cavity, said cam rotor rotating in the cavity having the tops of the two lobe portions thereof slightly spaced from the cylindrical inner surface of the cavity;
two vanes respectively and slidably received in two bores which are formed in diametrically opposed portions of said casing with respect to the axis of the cylindrical cavity, said bores being exposed to the cavity;
biasing means for biasing said two vanes toward the cam rotor so that the leading ends of the vanes are constantly in contact with the outer surface of the cam rotor; and
two pairs of inlet and outlet means which are associated with the diametrically opposed portions of said casing so that under rotation of the cam rotor, the fluid is introduced through said inlet into the cylindrical cavity and discharged therefrom into the outside through the outlet.
2. A fluid pump as claimed in Claim 1, further comprising a check valve operatively disposed in the outlet passage of each of said two pairs of inlet and outlet means, said check valve functioning to shut out the back flow of the fluid from the outside to the cavity, but permit forward flow from the cavity to the outside when the pressure in the cavity is higher than a predetermined degree.
3. A fluid pump as claimed in Claim 2, in which each of the vanes is arranged between the inlet and outlet passages of the corresponding one of the two pairs of inlet and outlet means.
4. A fluid pump as claimed in Claim 3, in which said top of each lobe portion of the cam rotor has a curved surface which is concentric with the cylindrical inner surface of the cavity of the casing.
5. A fluid pump as claimed in Claim 1, in which said biasing means is at least a spring which is disposed between the casing and the outside end of each vane.
6. A fluid pump as claimed in Claim 5, in which said spring has a fine winding portion at the casing side and a rough winding portion at the vane side.
7. A fluid pump substantially as hereinbefore described with reference to Figs. 3 to 6 of the accompanying drawings.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP699583A JPS59131793A (en) | 1983-01-19 | 1983-01-19 | Compressor for compressing vapor of cooling medium for engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| GB8401214D0 GB8401214D0 (en) | 1984-02-22 |
| GB2133837A true GB2133837A (en) | 1984-08-01 |
Family
ID=11653706
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| GB08401214A Withdrawn GB2133837A (en) | 1983-01-19 | 1984-01-17 | Rotary fluid-pump |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS59131793A (en) |
| DE (1) | DE3401064A1 (en) |
| GB (1) | GB2133837A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2207703A (en) * | 1987-07-20 | 1989-02-08 | Wang Liang Chih | Rotary fluid flow machine |
| GB2348673A (en) * | 1999-04-07 | 2000-10-11 | Alexander Orestovich Monfor | Power storing brake mechanism |
| GB2379482A (en) * | 2002-01-15 | 2003-03-12 | Alexander Orestovich Monfor | Hydraulic motor-generator |
| CN101649835A (en) * | 2008-08-12 | 2010-02-17 | 张金兰 | Method capable of improving rated working pressure of cam rotor vane pump |
| CN102155407A (en) * | 2011-04-21 | 2011-08-17 | 西安交通大学 | Single-cylinder dual-function rotary-type compressor |
| ITFI20130009A1 (en) * | 2013-01-10 | 2014-07-11 | Sigma Ingegneria S R L | ROTARY VOLUMETRIC PUMP |
| EP2646690A4 (en) * | 2010-11-29 | 2015-08-05 | Albert W Patterson | Rotary pump with a vane provided in each pump outlet |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112943601A (en) * | 2021-03-16 | 2021-06-11 | 大连绿鑫泵业有限公司 | Novel crocodile pump |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB733547A (en) * | 1953-11-24 | 1955-07-13 | Charles Scott Prendergast | Improvements relating to rotary pumps and motors |
| GB1464323A (en) * | 1974-06-06 | 1977-02-09 | Kunoti M | Rotary positive-displacement pump or motor |
| GB1554156A (en) * | 1976-06-09 | 1979-10-17 | Gec Elliott Mech Handling | Rotary positive displacement hydraulic machines |
-
1983
- 1983-01-19 JP JP699583A patent/JPS59131793A/en active Pending
-
1984
- 1984-01-13 DE DE19843401064 patent/DE3401064A1/en not_active Withdrawn
- 1984-01-17 GB GB08401214A patent/GB2133837A/en not_active Withdrawn
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB733547A (en) * | 1953-11-24 | 1955-07-13 | Charles Scott Prendergast | Improvements relating to rotary pumps and motors |
| GB1464323A (en) * | 1974-06-06 | 1977-02-09 | Kunoti M | Rotary positive-displacement pump or motor |
| GB1554156A (en) * | 1976-06-09 | 1979-10-17 | Gec Elliott Mech Handling | Rotary positive displacement hydraulic machines |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2207703A (en) * | 1987-07-20 | 1989-02-08 | Wang Liang Chih | Rotary fluid flow machine |
| GB2348673A (en) * | 1999-04-07 | 2000-10-11 | Alexander Orestovich Monfor | Power storing brake mechanism |
| GB2379482A (en) * | 2002-01-15 | 2003-03-12 | Alexander Orestovich Monfor | Hydraulic motor-generator |
| GB2379482B (en) * | 2002-01-15 | 2003-11-26 | Alexander Orestovich Monfor | Hydraulic motor-generator |
| CN101649835A (en) * | 2008-08-12 | 2010-02-17 | 张金兰 | Method capable of improving rated working pressure of cam rotor vane pump |
| EP2646690A4 (en) * | 2010-11-29 | 2015-08-05 | Albert W Patterson | Rotary pump with a vane provided in each pump outlet |
| CN102155407A (en) * | 2011-04-21 | 2011-08-17 | 西安交通大学 | Single-cylinder dual-function rotary-type compressor |
| ITFI20130009A1 (en) * | 2013-01-10 | 2014-07-11 | Sigma Ingegneria S R L | ROTARY VOLUMETRIC PUMP |
Also Published As
| Publication number | Publication date |
|---|---|
| GB8401214D0 (en) | 1984-02-22 |
| DE3401064A1 (en) | 1984-07-26 |
| JPS59131793A (en) | 1984-07-28 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| WAP | Application withdrawn, taken to be withdrawn or refused ** after publication under section 16(1) |