CN1032570A - Double-cranked reciprocating-piston model of engine - Google Patents
Double-cranked reciprocating-piston model of engine Download PDFInfo
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- CN1032570A CN1032570A CN 87103044 CN87103044A CN1032570A CN 1032570 A CN1032570 A CN 1032570A CN 87103044 CN87103044 CN 87103044 CN 87103044 A CN87103044 A CN 87103044A CN 1032570 A CN1032570 A CN 1032570A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/34—Ultra-small engines, e.g. for driving models
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Double-cranked reciprocating-piston model of engine, described type is the switching mechanism of the large and small bent axle that equates with crank radius r and the standard pitch diameter internal gear pair composition that equals two times and four times crank radius r respectively, with the to-and-fro motion of piston and the conversion mutually that rotatablely moves of bent axle, its piston does reciprocating linear motion by the rule of X=2r (1-cos α), and piston stroke equals the type of crank radius four times (X=4r).This type does not have connecting rod, the no piston side pressure to cylinder, and simple in structure, volume is little, and the efficient height can be used for two-stroke and the four-stroke petrol engine or the diesel engine of single cylinder or multi-cylinder, also can be used for compressor.
Description
The present invention relates to back and forth mesh the planetary rotation machine type, also relate to the multiple piston type type of connection rod-free reciprocating.
Existing conventional reciprocating piston type type, its to-and-fro motion realizes by connecting rod with the transformation that rotatablely moves.Adopt connecting rod to realize that the shortcoming of above-mentioned transformation is that connecting rod can produce bigger reciprocal inertia force, the centrifugal inertia force of the uneven part of rotary gadget and piston are to the side pressure of cylinder.Want the above-mentioned all power of balance, must cause the machine construction complexity, bulky, therefore, usually the reciprocal inertia force more than the secondary is not given balance, piston action is not married again yet or eliminated in the side pressure of cylinder, from kinematic viewpoint, this type is not too reasonable.Just there are many scientific workers to study the rotary-piston type type from earlier 1800s, the scheme that proposes reaches hundreds of (seeing " rotary piston engine " book that Science Press published in 1973), the also following kind of trial-produceing successfully surplus in the of ten, but it is all impracticable, to these world's sixties, many countries development triangle piston whirler,, because the problem of aspects such as structure, material and performance fails to properly settle, and have quite the conventional reciprocating piston type type of level and compare still for inferior.
The present invention is drawn (seeing " rotary piston engine " book that scientific and technological publishing house published in 1973) by type transform of Parsons invention in 1852, handkerchief is prohibited this type of once inventing with him, produce steamer, be used for driving on the ship generator, this machine stable working, not vibrations, but owing to cylinder will rotate, cause into, the complex structure of exhauster system, leakage vapour is serious, and overall dimension is very big, finally causes not conforming to practicality.The Parsons type is reasonable from kinematic viewpoint, and the structural type of piston and cylinder also is optimum scheme, and causing the basic reason that does not conform to practicality is owing to the cylinder rotation causes.
The present invention is in order to overcome the shortcoming that Parsons type cylinder will rotate, just handkerchief being prohibited in this type the rotating shaft of supporting the cylinder rotation makes bent axle into and (claims it to be large crankshaft in type of the present invention, to call large crankshaft in the following text), the bent axle that handkerchief is prohibited in this type (claims it to be small crankshaft in type of the present invention, to call small crankshaft in the following text), mode with revolute pair is connected on the crank pin of large crankshaft, so small crankshaft is as planet, divided by the small crankshaft journal axis is the center, outside the rotation, the journal axis of small crankshaft is the center rotation with the journal axis of large crankshaft also, thereby reaches that cylinder maintains static and purpose that machine can be worked.So just, draw the present invention-double-cranked reciprocating-piston model of engine.
The present invention compares the following characteristics that still have the Parsons type with the Parsons type:
(1) all movement parts are all done the uniform angular velocity rotation around a certain center fixing or rotation;
(2) piston does not have side pressure to cylinder;
(3) piston stroke equals four times of crank radius, and piston is also done straight reciprocating motion with the rule of X=2 γ (1-cos α);
(4) rotating speed of small crankshaft is two times of other movement parts rotating speed.
This type relatively has following advantages with conventional reciprocating piston type type:
(1) eliminated the side pressure of piston, caused cylinder:
1. mechanical loss reduces 20-30%;
Centering property improvement when 2. piston is worked in cylinder, lubricant oil is difficult for scurrying piston head, and the carbon residue in the cylinder amount reduces, and lubricant oil is economized;
3. the wearing and tearing of piston assembly and cylinder reduce, and the operating life of machine increases.
(2) quality of reciprocating part is little, only is equivalent to traditional again 1/3-1/2, has eliminated the above reciprocal inertia force of secondary simultaneously;
(3) cancelled connecting rod, the height of machine is reduced, the volume of crankcase diminishes, and can obtain higher scavenging pressure when being used for the two stroke diesel engine of crankcase scavenging, improves scavenge effect.
The present invention mainly is made up of cylinder (1), piston (3), cylinder cap (32), crankcase (4), axle sleeve (25), large crankshaft (10), small crankshaft (8), flywheel (19), internal gear (15), small gear (28).When being used for compressor, need set up lubrication system, cooling system, inlet and exhaust system.Then need have lubricated, cooling, inlet and exhaust system, distribution device and supply, devices such as ignition system if be used for internal-combustion engine.The most outstanding characteristics of the present invention are; Have large crankshaft and small crankshaft that crank radius γ equates and the standard pitch diameter of controlling these two bent axle relative positions and equal the internal gear pair that 2 times of crank radius γ and standard pitch diameter equal 4 times of crank radius γ; Moreover large crankshaft has at least in a bearing (as bearing (14)) is included in the crank of large crankshaft, to shorten the span of supporting point and Point of Strength.
The working principle of this type is: the internal gear (15) that the large crankshaft (10) that is equated by crank radius γ and small crankshaft (8) and standard pitch diameter equal 4 γ and standard pitch diameter equal the switching mechanism that the small gear (28) of 2 γ formed and realize the to-and-fro motion of piston (3) and the co-conversion mutually that rotatablely moves of large crankshaft (10).As shown in Figure 1, when large crankshaft (10) changeed the α angle counter clockwise, the journal axis of small crankshaft (8) was the arc length that γ α is rotated at the center with the journal axis of large crankshaft (10) just.Meanwhile, the crank pin of small crankshaft (8) is that 2 α angles are changeed at the center in the direction of the clock with the journal axis of small crankshaft (8).During this period, piston (3) is that the center is by counterclockwise rotation α angle, referring to accompanying drawing 1(a with the crank pin center line of small crankshaft (8) again) and (b); When large crankshaft (10) forwards α=90 ° to, be accompanying drawing 1(c) shown in situation; When large crankshaft (10) forwards to successively as accompanying drawing 1(d respectively), (e) and (f), get back to accompanying drawing 1(a then) situation, just constituted the once action of described switching mechanism, just go round and begin again backward.From accompanying drawing 1 as can be known the piston of this type (3) displacement do straight reciprocating motion by the rule of X=2 γ (1-cos α), the reciprocating stroke of its piston (3) is X=4 γ.
Working principle of the present invention can be summarized as follows:
1, the journal axis of small crankshaft (8) is the center rotation with the journal axis of large crankshaft, and its turning radius is the crank radius of large crankshaft (10) just;
2, the crank pin of small crankshaft (8) is the center rotation with the journal axis of small crankshaft (8) again, it turns to opposite with large crankshaft (10), rotating speed is the twice of large crankshaft (10) rotating speed, and the crank radius of small crankshaft (8) must equal the crank radius of large crankshaft (10);
3, piston (3) is the center rotation with the crank pin center line of small crankshaft (8), and it turns to all identical with large crankshaft (10) with rotating speed;
4, the turning to of described large crankshaft (10) and small crankshaft (8), rotating speed are controlled with a pair of internal gear pair; And piston (3) will be play the guiding role to piston (3) by cylinder (1) with the rotation of the crank pin center line of small crankshaft (8) and controls;
5, the rotation of described revolving part, as long as there is one to be when at the uniform velocity rotating, remaining two also must be at the uniform velocity to rotate.
This type can be used for two-stroke and the four-stroke petrol engine or the diesel engine of single cylinder or multi-cylinder, also can be used for the compressor of single cylinder or multi-cylinder.This type is used for the slow-speed of revolution, and even cylinder symmetry (" I " type) can obtain higher mechanical efficiency when arranging.This type is compared with conventional reciprocating piston type type, under the situation of same cylinder diameter, stroke, rotating speed, its external dimension are then than about traditional little sixth of reciprocating piston type type, and owing to the side pressure of no piston to cylinder, its mechanical efficiency is also than conventional reciprocating piston type type height.
Essence of the present invention is: replace the connecting rod of traditional reciprocating piston type type with dual crank mechanism, thereby reach the raising gear efficiency, increase working life, dwindle the machine volume, alleviate the purpose of machine weight.
Description of drawings:
Accompanying drawing 1 is the reciprocating type type working principle of an a kind of dual crank sketch;
Accompanying drawing 2 is the double crank reciprocating piston formula compressor general assembly drawing of a kind of vertical, single cylinder, air-cooled and splash lubrication, and each label is respectively among its figure:
(1) cylinder; (2) piston ring; (3) piston; (4) crankcase; (5) front cover; (6) screw; (7) ring washer; (8) small crankshaft; (9) bearing shell; (10) large crankshaft; (11) balance iron; (12) oil drain plug; (13) springhole ring washer; (14) rolling bearing; (15) internal gear; (16) rolling bearing; (17) rear end cover; (18) oil sealing; (19) fan wheel of band flywheel; (20) belt pulley; (21) screw; (22) nut; (23) packing ring; (24) key; (25) axle sleeve; (26) ring washer; (27) bearing shell; (28) small gear; (29) outlet pipe; (30) key; (31) tongue method; (32) cylinder head; (33) air-strainer.
Accompanying drawing 5 is the small crankshaft view;
Accompanying drawing 6 is the internal gear view;
Accompanying drawing 7 is the axle sleeve view;
Accompanying drawing 8 is the small gear view;
Accompanying drawing 9 is piston shaft mapping and sectional view;
Accompanying drawing 10 is a kind of type simplified schematic diagram of cylinder linear array, and each label is respectively among its figure:
(8-1,8-2,8-3) three small crankshafts;
The crank of (10-1,10-2,10-3) three pairs of large crankshafts;
(15-1,15-2,15-3,15-4,15-5,15-6) six internal gears;
(28-1,28-2,28-3,28-4,28-5,28-6) six small gears;
(14-1,14-2,14-3) three pairs of bearings that contain the large crankshaft crank;
(1-1,1-2,1-3,1-4,1-5,1-6) six cylinders;
Accompanying drawing 11 is the type simplified schematic diagram that a kind of cylinder V-type is arranged, and each label is respectively among its figure:
(3-1,3-2) two pistons;
Two cranks on (8-1,8-2) small crankshaft;
(10) crank of large crankshaft;
Accompanying drawing 12 is the type fundamental diagram that a kind of cylinder V-type is arranged;
Accompanying drawing 13 is the dual crank diesel engine general assembly drawing of a kind of vertical, single cylinder, air-cooled, splash lubrication.Wherein each label is respectively:
(1) cylinder; (2) piston ring; (3) piston; (4) crankcase; (5) end cap; (8) small crankshaft; (9) bearing shell; (10-1,10-2) large crankshaft; (11) balance iron; (12) oil drain plug; (13) springhole ring washer; (14) rolling bearing; (15) internal gear; (16) rolling bearing; (18) oil sealing; (20) belt pulley; (25) axle sleeve; (29) outlet pipe; (32) cylinder cap; (33) air-strainer; (34) elastic axis ring washer; (36) flywheel; (37) large crankshaft timing gear; (39) starting melon; (40) timing idle pulley; (41) v belt; (42) axial fan.
Below in conjunction with accompanying drawing embodiment is described:
Embodiment 1:
The double crank reciprocating piston formula compressor (abbreviation compressor) of a kind of vertical, single cylinder constructed in accordance, air-cooled, splash lubrication.Structure such as accompanying drawing 2, piston (3) adopt aluminum alloy ZL108; Large crankshaft (10) and small crankshaft (8) are used spheroidal graphite cast iron QT50-1.5; Internal gear (15) and small gear (28) are with No. 45 steel; Fan wheel foundry goods such as (19) HT20-40 of cylinder (1), axle sleeve (25), crankcase (4), cylinder cap (32), band flywheel; Other pieces are made material with Common Straight Carbon Steel or Fine Steel Casting iron respectively.This compressor: cylinder bore=90mm; Piston stroke X=80mm; Rotating speed is that 800 γ pm discharge capacities are 0.3m
3/ min; Rated pressure is 7kgf/cm
2Use the 2.2KW motor drives.
Accompanying drawing 3 has provided interior each parts assembly drawing of axle sleeve (25) of this compressor.Main parts in addition in the axle sleeve (25) are seen accompanying drawing 4,5,6,7,8,9 respectively.
Embodiment 2:
The double crank reciprocating piston formula diesel engine (abbreviation diesel engine) of a kind of vertical, single cylinder as shown in figure 13, air-cooled, splash lubrication.Now the compressor with this diesel engine and embodiment 1 contrasts, so that understand its structure situation:
(1) because diesel engine has distribution device, so the cylinder cap of diesel engine (32) is all different with profile with its internal structure of cylinder cap (32), the device of compressor;
(2) because the camshaft of distribution device is mounted in front shaft sleeve (25) and crankcase (4) lining, diesel engine has oil supply system simultaneously, the Injection Pump of oil supply system will be driven by large crankshaft, therefore the structure shape of front shaft sleeve (25) is different with axle sleeve (25) structure shape of compressor, and the shape of crankcase (4) back is also different;
(3) camshaft of diesel engine and Injection Pump will be driven by large crankshaft, and crankshaft timing gear (37), timing idle pulley (40) and fuel injection pump gear (cuing open in accompanying drawing 13) therefore are housed on the axle journal of front end large crankshaft (10-1);
(4), on front end large crankshaft (10-1) and rear end large crankshaft (10-2), all has only one so support its bearing because the axle journal of the small crankshaft (8) of diesel engine is distributed in the both sides of its crank pin;
(5) the axle journal external part of diesel engine front end large crankshaft (25) is the belt pulley (20) and the starting melon (39) of affixed drive axial fan (42), and flywheel (36) is the external part that is fixed in rear end large crankshaft (25), and these are also different with compressor;
(6) rear axle housing of diesel engine is owing to its inner large crankshaft (10-2) of installing will be lacked, so also the ratio piston compressor axle sleeve is short for rear axle housing.So should be as shown in Figure 13.
The type (hereinafter to be referred as straight line type) of a kind of cylinder linear array as shown in Figure 10, this type has: three small crankshafts, four large crankshafts; Cylinder (1-1) and (1-2) shared small crankshaft (8-1), cylinder (1-3) and (1-4) shared small crankshaft (8-2), cylinder (1-5) and (1-6) shared small crankshaft (8-3); The crank of large crankshaft (hereinafter to be referred as big crank), (10-1) and small crankshaft (8-1) link, big crank (10-2) and small crankshaft (8-2) link, big crank (10-3) links with small crankshaft (8-3); Big crank (10-1), (10-2) and (10-3) be mutually 120 are shown in the right figure of accompanying drawing 10; Type shown in the accompanying drawing 10 have six pairs of internal gear pairs (28-1,15-1), (28-2,15-2), (28-3,15-3), (28-4,15-4), (28-5,15-5) and (28-6,15-6); Be used for quartastroke engine as above-mentioned straight line type, it turn to as shown in Figure 10 that big crank rotates counter clockwise, if its ignition order is (1-1)-(1-5)-(1-3)-(1-6)-(1-2)-(1-4); (also can be orders such as (1-1)-(1-6)-(1-4)-(1-2)-(1-5)-(1-3) carries out).When crank, piston were in position shown in Figure 10: (1-1), (1-4) cylinder is power stroke, (1-5) cylinder was a compression stroke.(1-6) cylinder is an exhaust stroke, (1-2), (1-3) cylinder is aspirating stroke.Below discuss its working order with regard to above-mentioned situation:
(1) piston in the cylinder (1-4) is subjected to the effect of gaseous-pressure, move down and just promote small crankshaft (8-2) and clockwise rotate, see accompanying drawing 10 right figure, small crankshaft (8-2) rotation drives small gear (28-3), (28-4) rotate, because small gear (28-3) is a pair of intermeshing internal gear pair with internal gear (15-3), small gear (28-4) also is a pair of intermeshing internal gear pair with internal gear (15-4), and internal gear (15-3), (15-4) be the fixed block that is fixed in the body again, so small gear (28-3), (28-4) rotate and just can only drive big crank (10-2) and (the 10-1 right side) and reach (a 10-3 left side) and rotate counter clockwise (because of big crank (the 10-1 right side) and big crank (a 10-2 left side) are two cranks on the same large crankshaft; Big crank (a 10-3 left side) and big crank (the 10-2 right side) also are two cranks on the same large crankshaft).The rotation of big crank (the 10-1 right side) is because internal gear pair (28-2, effect 15-2), forcing small crankshaft (8-1) to make clockwise direction rotates, (28-1 under effect 15-1), forces large crankshaft (a 10-1 left side) to rotate counter clockwise again at internal gear pair.The rotation of big crank (a 10-3 left side) is because internal gear pair (28-5, effect 15-5), forcing large crankshaft (8-3) to make clockwise direction rotates, (28-6 under effect 15-6), forces large crankshaft (the 10-3 right side) to rotate counter clockwise again at internal gear pair.The straight line motion of piston is transformed into rotatablely moving of bent axle like this.
(2) as shown in figure 10, (1-1) cylinder also is in power stroke, but (1-1) at this moment the piston of cylinder is positioned at upper dead center, and (1-1) gaseous-pressure in the cylinder can't promote small crankshaft (8-1) and big crank (10-1) rotation.At this moment be to rely on above-mentioned (1-4) cylinder inner carrier to be subjected to the effect of gaseous-pressure, three small crankshafts all are rotated in a clockwise direction, four large crankshafts are all along counterclockwise rotation, rotation when small crankshaft (8-1) and big crank (10-1), make (1-1) and (1-2) cylinder turn over after top dead center, in (1-1) cylinder of power stroke, its gaseous-pressure just promotes piston to lower compression small crankshaft (8-1), quicken to rotate along clockwise direction, small crankshaft (8-1) drives small gear (28-1,28-2) rotate, because small gear (28-1), (28-2) be fixed on the internal gear (15-1) in the body and (15-2) be meshed, also just force big crank (10-1) and (a 10-2 left side) to be rotated counter clockwise, thereby drive other cylinder operation.When big crank (10-1), (10-2) and (10-3) rotating 120 degree angles, cylinder (1-5) just catches fire and enters power stroke.
Accompanying drawing 10 below the major axis that also drawn, gear has all been adorned at this two ends.These two gears are meshed with gear on being fixed in internal-combustion engine initial and end large crankshaft axle journal, make the rotation of each large and small bent axle more harmonious thereby its effect is the torque of balance internal-combustion engine two ends large crankshaft.In fact this root axle is not that design is to bear this task by the camshaft of motor at the oil sump position of motor.
Figure 11 arranges schematic representation for angle between banks become 90 ° V-type.Wherein (10) represent the large crankshaft crank; (8-1) and (8-2) represent that (1-1) cylinder reaches (1-2) the small crankshaft crank of cylinder; (3-1) and (3-2) expression (1-1) cylinder and (1-2) piston of cylinder, (1-1) shown in the figure cylinder and (1-2) the crank angle of the small crankshaft of cylinder be 180 °.
Figure 12 is the kinematic sketch that Figure 11 V-type is arranged.Two cylinders are shared big cranks among the figure, must equate with the crank radius of large crankshaft according to the crank radius of the principle small crankshaft of this type, now only see a cylinder, just can understand its motion conditions fully.Now see the piston of the cylinder on Figure 12 the right, the initial position of supposing machine is shown in Figure 12 (a), when big crank with counterclockwise rotation α angle, small crankshaft then with its body journal axis be the center by clockwise commentaries on classics 2 α angles, piston is that the center is by counterclockwise rotation α angle with the crank pin of small crankshaft again.Shown in Figure 12 (b), when large crankshaft α=45 °, small crankshaft just changes 90 ° in the direction of the clock, and the piston duty is beaten speech and closed 5 ° of Guangs, then large and small bent axle and position of piston.By accompanying drawing 12(b) enter (c), accompanying drawing 12(d), (e) and (f) be crank pin when the large crankshaft situation when changeing 90 °, 180 ° and 225 ° counter clockwise, when large crankshaft changes 360 °, each moving element is got back to accompanying drawing 12(a again) shown in the position.
The rotation of above-mentioned each parts is carried out simultaneously, so the absolute motion of piston do not rotate, but moves as straight line.
Can draw the type that inblock cylinder is classified " X " type and " I " type as from the working principle of above " V " type machine.
Claims (6)
1, double-cranked reciprocating-piston model of engine, it is by cylinder (1), piston (3), crankcase (4), bent axle (8,10), internal gear pair (15,28), axle sleeve (25), cylinder cap (32), flywheel (19), balance iron compositions such as (11); It is characterized in that described bent axle (8,10) is made up of large crankshaft (10) and small crankshaft (8) that crank radius r equates, small crankshaft (8) is installed on the crank pin of large crankshaft (10), connects in the mode of revolute pair; Its afterbody of described piston (3) is that bearing connects with the crank pin of small crankshaft (8), constitutes revolute pair; Described internal gear pair (15,28) equals the small gear (28) of 2 times of crank radius r by standard pitch diameter and internal gear that standard pitch diameter equals 4 times of crank radius r is formed; Described small gear (28) is fixed in the axle journal middle part or the end of small crankshaft (8), and internal gear (15) is fixed in the interior float chamber of axle sleeve (25) (4); After cylinder of described type (1) and axle sleeve (25) assembled with crankcase (4), the integral body of formation must be the center line of cylinder (1) and the bearing hole center line quadrature that axle sleeve (25) inwall is installed large crankshaft (10); The bearing (14,16) of described large crankshaft (10) has at least in a crank large crankshaft is included in, as bearing (14).
2, type as claimed in claim 1, it is characterized in that cylinder (1), crankcase (4), axle sleeve (25) are single part or an integral body in addition, perhaps cylinder (1) is as a whole with crankcase (4), and perhaps axle sleeve (25) is an integral body with crankcase (4).
3, type as claimed in claim 1 is characterized in that it is equipped with the oil supply system of internal-combustion engine, lubrication system, cooling system, advances exhauster system and ignition mechanism.
4, type as claimed in claim 1 is characterized in that it is equipped with the air inlet system and exhaust system of compressor, lubrication system and cooling unit.
5, type as claimed in claim 1, it is characterized in that constituting all bearings that revolute pair connects is sliding bearing or rolling bearing.
6, type as claimed in claim 1, it is characterized in that it be single cylinder or multi-cylinder, the linearly type of multi-cylinder, " V " type, " X " type, " I " type are arranged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 87103044 CN1032570A (en) | 1987-10-13 | 1987-10-13 | Double-cranked reciprocating-piston model of engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 87103044 CN1032570A (en) | 1987-10-13 | 1987-10-13 | Double-cranked reciprocating-piston model of engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1032570A true CN1032570A (en) | 1989-04-26 |
Family
ID=4814253
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 87103044 Pending CN1032570A (en) | 1987-10-13 | 1987-10-13 | Double-cranked reciprocating-piston model of engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1032570A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1055119C (en) * | 1996-06-05 | 2000-08-02 | 南京农业大学 | Chemical residual degradation vaccine and its prodn. method |
| CN1056407C (en) * | 1995-06-30 | 2000-09-13 | 齐涵 | Live bacteria preparation containing Bacillus subtilis and its application in treatment of burns |
| CN104845906A (en) * | 2015-03-26 | 2015-08-19 | 湖南农业大学 | Bacillus licheniformis for preventing and treating grape downy mildew |
-
1987
- 1987-10-13 CN CN 87103044 patent/CN1032570A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1056407C (en) * | 1995-06-30 | 2000-09-13 | 齐涵 | Live bacteria preparation containing Bacillus subtilis and its application in treatment of burns |
| CN1055119C (en) * | 1996-06-05 | 2000-08-02 | 南京农业大学 | Chemical residual degradation vaccine and its prodn. method |
| CN104845906A (en) * | 2015-03-26 | 2015-08-19 | 湖南农业大学 | Bacillus licheniformis for preventing and treating grape downy mildew |
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