Source: https://patents.google.com/patent/DE4134399B4/en
Timestamp: 2020-06-03 07:44:21
Document Index: 419030141

Matched Legal Cases: ['art 18', 'art 29', 'art 29', 'art 18', 'art 29', 'art 29', 'art 18', 'arts 29', 'art 18', 'art 29', 'art 29', 'art 18', 'art 18']

DE4134399B4 - Compensation device for a motor - Google Patents
Compensation device for a motor
DE4134399B4
DE4134399B4 DE19914134399 DE4134399A DE4134399B4 DE 4134399 B4 DE4134399 B4 DE 4134399B4 DE 19914134399 DE19914134399 DE 19914134399 DE 4134399 A DE4134399 A DE 4134399A DE 4134399 B4 DE4134399 B4 DE 4134399B4
DE19914134399
DE4134399A1 (en
Hiroyuki Kawagoe Kawakubo
Shinichi Kawagoe Nakano
Toshio Shiki Shimada
Hiroshi Kiyose Wakoh
1990-10-18 Priority to JP2-280152 priority Critical
1990-10-18 Priority to JP28015290A priority patent/JP3071815B2/en
1991-10-17 Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
1992-04-23 Publication of DE4134399A1 publication Critical patent/DE4134399A1/en
2006-08-10 Publication of DE4134399B4 publication Critical patent/DE4134399B4/en
Drive device for a motor vehicle with an engine (1), a crankshaft (8) and a transmission (36),
(a) a pair of primary balancing weights (22, 35) rotating at the same speed of the crankshaft (8) and a secondary balancing weight (44, 47) rotating at twice the speed of the crankshaft (8);
(b) a first balancer shaft (15) and a second balancer shaft (16) both located near and parallel to the crankshaft (8), the first (15) and second (16) balancer shafts from the crankshaft via gears (Fig. 19, 26, 34) are driven, wherein on the first balance shaft (15) two balance weights (22; 44) are arranged, namely one (22; 44) of the pairs of primary and secondary balance weights (22, 35, 44, 47) and wherein the one remaining balance weight (35) of the pair of primary balance weights (22, 35) is disposed on the second balance shaft (16), and
(c) a close and parallel to the second balance shaft ...
The The invention relates to a drive device for a motor vehicle according to the features the preambles of the claims 1 and 4.
Examples compensation devices for reduction by the drive motor caused vibrations are for example from JP 60-155033 AA and the JP 50-132309 A1.
at the compensating device of the first-mentioned patent application at parallel to the crankshaft arranged balance shafts respectively attached a pair of balance weights. Secondary vibrations of the engine will be through opposing Rotation of counterweights of each equalizer with the double Speed of the crankshaft damped.
at Single-cylinder engines, the effects of primary vibrations are particularly severe. therefore you do not just need the secondary, but also the primary, dampen vibrations caused by the engine.
If in a single-cylinder engine, such balancing means for primary vibrations must exist separately from the secondary vibration compensator provide a pair of balance shafts and the second balance shafts at the same speed as the crankshaft and in the same direction rotate. Because you are for the secondary Compensation device must provide a special room, this leads Construction to many problems, such as the complexity of transmission the rotational forces necessary mechanisms and a general loss of freedom of design possibilities.
According to the second mentioned Patent application is parallel to the crankshaft of the engine a pair of balance shafts arranged. At each of the balance shafts are balance weights attached. Each of the balancing weights is in a predetermined Coordinate range of the crankshaft arranged.
at In this arrangement, the balance weights of the pair of balance shafts become with the double speed and the crankshaft and turned in opposite directions, around the secondary vibrations of the To dampen the engine. By arranging the balance weights within a certain Area of the crankshaft are the through the head and cylinder sections The vibration generated by the engine simultaneously damped.
These Technology has the following disadvantages. Because the balance shafts in one predetermined range must be arranged relative to the crankshaft goes lost design freedom in the engine design.
If continue to change the engine volume should, must the balance shafts are rearranged because the vibration moments the head and cylinder sections by changing the engine volume also change. Thus, the desired Basic structure of the engine lost. In addition, there are the following general problems more conventional Motor balancing technique. In single-cylinder engines, the moment of inertia be high enough to be quiet due to low vibration To reach driving mode.
In order to increase the moment of inertia of the crankshaft, the following is generally desirable:
1. Increase of the outer diameter of a pair of balance weight sections attached to the crankshaft
2. increasing the thickness of the pair of balance weights in the axial direction of the crankshaft;
3. Magnification of the flywheel attached to the crankshaft.
If However, if one pursues the first goal, the center distance between the crankshaft and the transmission main shaft are enlarged to one another mechanical interference with the crankshaft and the balance weight sections to avoid. But this leads to the undesirable Result that the size and that Increase the weight of the engine. An increase in the moment of inertia of the crankshaft can be further achieved by the balancing mass from the axial center of the crankshaft farther away. But if one pursues the second goal, then the increase of the moment of inertia compared to the required weight increase the crankshaft relatively low because of the outer diameter of the balance weight sections is kept low. Going to the third goal, this leads to vibration problems caused by torsional or bending forces on the Crankshaft. A stiffening of the crankshaft by enlargement leads to undesirable Weight increase.
Out FR-2633995 A1 is a compensating device according to the preamble from claim 1 and 4 known. There is the power transmission system for the primary balancing weights arranged in a first plane, while respective power transmission systems for the both secondary Balance weights are arranged in two further levels. Further wear this second driven gear that is integral with the secondary balance weight, no further moment compensator.
task The invention is, with little effort, especially in single-cylinder engines to achieve a quiet engine run.
The object is achieved by a balancing device that dampens dynamic vibrations in a motor vehicle with an engine, a crankshaft and a transmission by a balancing device. The balancing device comprises according to claim 1:
(a) a pair of primary crankshaft rotating at the same speed primary balancing weights and a pair of crankshaft rotating crankshaft rotating secondary balancing weights, (b) a first balancer shaft and a second balancer shaft both disposed close to and parallel to the crankshaft; first and second balancer shafts are driven by the crankshaft by means of gears, two balance weights being disposed on the first balancer shaft, one of the pairs of primary and secondary balancers, and the one remaining balancer weight of the primary balancer pair being disposed on the second balancer shaft; and (c) a third balancer shaft disposed proximate and parallel to the second balancer shaft and driven by gears via the second balancer shaft, the remaining balancing weight of the secondary balancer pair being disposed on the third balancer shaft, where the positional relationships of the components are: L1: L2: L3 = 1.5: 1.5: 1 where the symbols L1, L2 and L3 denote the distances between the components as follows: L1 the center distance between the first balance shaft and the crankshaft, L2 the center distance between the crankshaft and the second balance shaft and the center distance between the second balance shaft and the third balance shaft, characterized in that respective power transmission systems for the primary and secondary balance weights are arranged in each case in a common plane.
By the above choice of the center distances between the crankshaft and the balance shafts, the following is achieved according to the invention:
By disposing one of the primary balance weights and one of the secondary balance weights having different rotational speeds from each other on the same axis, at least one shaft is saved between the primary and secondary balance weight portions. This leads to a reduction in space requirements.
Further is in the arrangement of the power transmission system the primary and secondary Balancing equipment in one plane too complex a motor structure prevents, thereby reducing the dimensions of the power transmission path of the crankshaft the balance shafts are minimized.
The invention further relates to a drive device for a motor vehicle with an engine, a crankshaft and a transmission. The drive device comprises according to claim 4:
(a) a balance shaft arranged close to and parallel to the crankshaft with a first driven gear integral therewith and a second driven gear rotatable about the balance shaft;
(b) a primary gear and a drive gear disposed on the crankshaft, the primary gear for transmitting drive force to the balance shaft, to the first driven gear, and the drive gear to be engaged with the second driven gear,
(c) a primary balancing weight disposed on the balancer shaft and dampening engine vibrations during rotation;
(d) a secondary balancer weight integral with the second driven gear and dampening motor vibrations during rotation;
characterized in that the mass of the second driven gear is distributed in the radial direction so that it forms a moment compensator for damping engine vibrations, wherein the torque compensator is formed integrally with the driven gear such that the torque compensator of the driven gear in the axial direction thereof protrudes.
According to this Aspect of the invention, engine vibrations are even more effective thereby steamed, that one of the pair of torque compensation devices on the the same axis as that of the balance weights to the secondary component to zero. The secondary component reaches its peak during of the vibration moment generated by the combustion process.
The Invention will be described below with reference to an embodiment on the attached Drawings described.
1 shows a sectional view of the left side of a motor;
2 shows a partially sectioned view of the right side of the engine after 1 ;
3 shows a sectional view in a plane according to III-III in 1 ;
4 shows a sectional view in a plane according to IV-IV in 2 ; and
5 shows a sectional view in a plane to VV in 4 ,
An engine 1 For example, a single-cylinder four-stroke engine includes a crankcase 2 , a cylinder block 3 , one on the cylinder block 3 attached cylinder head 4 , one on the cylinder head 4 attached head cover 5 and one on the cylinder head 4 attached and connected via a passage with the head carburetor 6 ,
In the crankcase is a balancer 7 added. Approximately in the middle of the crankcase 2 is how in 3 shown a crankshaft 8th over a pair of bearings 99 and 10 on the crankcase 2 freely rotatably held. The crankshaft 8th has a crank pin 8a , which has a connecting rod 12 with a slidable piston 11 connected is.
At that by the camp 9 from the crankcase 2 protruding end of the crankshaft 8th is a rotor 13a a generator 13 attached. In the rotor 13a is a stator 13b arranged along with a on the outer surface of the crankcase 2 to be mounted generator cover 14 the generator 13 form.
As in the 1 and 3 is represented by the other bearing 10 from the crankcase 2 by protruding opposite end of the crankshaft 8th a primary gear 19 attached, which has both a first balancer shaft 15 as well as an outer coupling part 18 one on a main shaft 16 attached clutch 17 rotating drives. The main shaft 16 also serves as a second balance shaft.
The first balance shaft 15 is parallel to the crankshaft 18 arranged and, as in 3 represented by a pair of bearings 20 . 21 in the crankcase 2 freely rotatably held. Both ends of the balance shaft 15 stand out of the crankcase 2 in front.
At one end of the first balance shaft 15 is in the axial direction of the shaft 15 a spline 15a intended. This spline 15a prevents relative rotation 1 a first primary balance weight 22 a pair of primary balancing weights, that on the first balancer shaft 15 by means of one on the one end of the first balance shaft 15 screwed nut 23 is attached. The first primary balance weight 22 is therefore outside the camp 20 and the crankcase 2 arranged.
At the out of the crankcase 2 protruding opposite end of the first balance shaft 15 is a collar 24 by means of a mother 25 attached. On the collar 24 is a driven gear 26 attached, its teeth with the primary gear 19 the crankshaft 8th engage.
By this arrangement, the rotation of the crankshaft 8th over the primary gear 19 and the driven gear 26 on the first balance shaft 15 transmit, thereby reducing the first balance weight 22 in the same direction of rotation of the crankshaft 8th is turned.
The main shaft 16 is how in 1 and 3 represented, parallel to the crankshaft 8th and at the first balancer shaft 15 arranged opposite side of the crankshaft. The main shaft 16 is in the crankcase 2 over a pair of bearings 27 . 28 freely rotatably held. The one end of the main shaft 16 is inside the crankcase 2 arranged while their opposite end through the camp 28 from the crankcase 2 protrudes like this in 3 you can see.
At the protruding end of the main shaft 16 is an inner coupling part 29 the clutch 17 by means of a spline and a nut 30 attached to a relative rotation of the inner coupling part 29 to the main shaft 16 to prevent.
The outer coupling part 18 largely surrounds the inner coupling part 29 and is on the outer periphery of the protruding end of the main shaft 16 freely rotatably mounted.
Between the inner coupling part 29 and the outer coupling part 18 are in the axial direction of the main shaft 16 one after the other several annular coupling plates 31 arranged. These coupling plates 31 Can with the inner and outer coupling parts 29 and 18 are mutually engaged in the circumferential direction.
Between the outer coupling part 18 and the inner coupling part 29 is one along the main shaft 16 in the axial direction free sliding pressure plate 32 arranged to thereby by means of clutch springs 33 generated biasing forces the clutch plates 31 in the inner coupling part 29 to press.
As in 3 is shown on the crankcase side of the outer coupling part 18 a driven gear 34 attached to the primary wheel 19 is in attack and on the main shaft 16 is freely rotatably mounted. The driven gear 34 , the outer coupling part 18 and the second primary balance weight fitted between these two 35 are about to turn around the main shaft 16 connected with each other.
Therefore this second primary balancing weight is 35 outside the crankcase 2 and the first primary balance weight 22 arranged opposite and is through the crankshaft 8th in the opposite direction of rotation of the crankshaft 8th turned.
The crankshaft 8th , the first balance shaft 15 and the main shaft 16 are arranged relative to each other so that the center distance L1 between the crankshaft 8th and the first balance shaft 15 equal to the axial distance L2 between the crankshaft 8th and the main shaft 16 is.
The number of teeth of the primary gear 19 and both driven gears 26 . 34 are equal, reducing the primary balancing weights 22 and 35 at the same speed as the crankshaft 8th but turn in opposite direction to it.
The motor 1 is with a gearbox 36 provided, which is the main shaft 16 as a structural element.
The gear 36 is inside the crankcase 2 arranged and provided with: one parallel to the main shaft 16 arranged countershaft 37 serving as a third balance shaft, a set between the main shaft 16 and the countershaft 37 arranged gear change wheels 38 a plurality for selectively operating the speed change wheels 38 actuated shift forks 39 , one the shift forks 39 moveable leading shaft 40 , one with each shift fork 39 Switching drum connected to the circuit 41 and one the shift drum 41 rotating driving shaft 42 ,
Next is the crankcase 2 the first balance shaft 15 all around as well as on the countershaft 37 a secondary equalizer 43 accommodated.
The secondary equalizer 43 has the following components: a first secondary balance weight 44 a pair of secondary counterbalance weights, the periphery of the first balancer shaft 15 is freely rotatably mounted, one with the first secondary balance weight 44 integral driven gear 45 , one with the crankshaft 8th firmly connected drive gear 46 , a second secondary counterweight 47 of the pair of secondary counterbalance weights, on the circumference of one, within the crankcase 2 arranged end of the countershaft 37 freely rotatably mounted, one with the second secondary balance weight 47 integral driven gear 48 and an idler 49 that with both the crankshaft 8th attached drive wheel 46 as well as with the driven gear 48 of the second secondary balance weight 47 engaged.
An axial distance between the main shaft 16 and the countershaft 37 and an axial distance L1 between the crankshaft 8th and the first balance shaft 15 are in the relationship L1 = 1.5 · L3. The number of teeth of the driven wheels 45 . 48 is the same as that of the idler 49 while the drive wheel 46 the double number of teeth of the driven wheels 45 . 48 and the idler 49 Has.
When the crankshaft 8th turns, turn the secondary balance weights 44 . 47 with twice the speed of the crankshaft 8th , This turns the second secondary counterweight 47 in the same direction as the crankshaft 8th while getting the first secondary balance weight 44 against the crankshaft 8th rotates.
The diameter of the second secondary balance weight 47 receiving area of the countershaft 37 is greater than the diameter of its gearing area where the set of gear change wheels 38 is appropriate.
The reason for this difference in diameter is that the area of the countershaft 37 , the one by rotation of the second secondary balance weight 47 is reinforced and subjected to a bending moment exerting centrifugal force, is amplified and a reduction of the effective diameter of the countershaft 37 reached.
As in the 1 and 3 is shown on the at the first balancer shaft 15 rotatably mounted driven wheel 45 a first moment compensator 50 a pair of moment balancer 50 . 51 integrally formed. Therefore, the first torque equalizer is running 50 on the same axle as the first secondary counterweight 44 ,
As in the 1 and 3 is shown on the main shaft 16 freely rotatable idler 49 a second moment compensator 51 of the pair of moment balancers 50 . 51 integrally formed.
In the set gear change wheels 38 Gear trains G1-G5 are formed for five gears, composed of on the main shaft 16 arranged wheels 52 to 56 , where the wheel 52 of the first-speed gear train G1 has the smallest diameter and this gear train G1 has the largest speed-reduction ratio. A right balance weight section 58 a pair left and right balance weight sections 57 . 58 the crankshaft 8th is just a short distance from the wheel 52 smallest diameter of the gear train G1 arranged for the first gear. The left balance weight section 57 is with only a small distance from the peripheral area of the wheels 54 . 55 larger diameter of the gear trains G3 and G4 arranged. The outer diameter of the right balance weight portion 58 greater than that of the left balance weight section 57 and the right balance weight portion 58 thinner than the left balance weight section 57 , By increasing the outer diameter and reducing the thickness of the right balance weight portion 58 one can increase the moment of inertia, which changes in proportion to the second power of the radius, even if the weights of the two balance weight sections 57 . 58 stay the same.
The right end of the first balance shaft 15 is with a water pump shaft 59 connected to a part of a water pump 60 to the circulation of water forms.
At the top of the cylinder block 3 is a cylinder head 9 attached, of a combustion chamber 100 forms and an inlet opening 101 and an outlet opening 102 contains, which in each case intake and exhaust valves 103 and 104 assigned. At the top of the crankcase 2 is a starter motor 105 appropriate. The right side of the crankcase 2 is by a removable crankcase cover 112 closed, from the small part through a small side cover 113 is closed.
As already described above, that is through the bearing pair 9 and 10 in the crankcase 2 held crankshaft 8th in their midrange with the pair of balance weight sections 157 . 158 Mistake. The pair of balance weight sections 157 . 158 is through a crankpin 8a connected to the via a needle bearing 120 the larger end portion of the connecting rod 12 connected. At the left end. the crankshaft 8th is the generator 13 attached, which also serves as a flywheel and on the axial inside of a ring gear 122 attached, in turn, by the starter motor 105 to start the engine 1 is drivable. The primary gear 19 is fixed to the right side of the crankshaft 8th connected to the torque through the clutch 17 to transfer to the transmission. One with the right part of the crankshaft 8th connected pump drive shaft 124 ( 4 ) is at one an opening of the crankcase 2 covering the crankcase cover 112 freely rotatably held. The pump drive axle 124 carries a trochoid oil return pump 125 and an oil pump 126 ,
The structural features of the oil return pump 125 be regarding the 4 and 5 explained. On the inner surface of the crankcase cover 112 is an annular, to the drive axle 124 eccentric recess 127 formed as part of the pump housing. The annular recess 127 freely rotatably supports an outer rotor 128 with internal teeth, with external teeth of an internal motor 129 engage. The inner rotor 129 is with the pump drive axis 124 firmly connected. The crankshaft 8th facing side surface of the two rotors is with a side plate 130 covered. Between the inner rotor 129 and the outer rotor 128 are several operating chambers 131 their volume when turning the drive axle 124 can change. On the inside of the crankcase cover 112 is an inlet port 132 , the volume expansion page of the chambers 131 facing, and an outlet opening 133 , the volume contraction side of the chambers 131 facing, arranged. Down in the crankcase 2 is an oil reservoir 135 with a sieve filter 134 arranged. The oil reservoir communicates with the inlet port 132 via one on the inside of the crankcase cover 112 formed oil passage 136 in connection. The outlet opening 133 is over an oil passage 137 and one on the inside of the crankcase cover 112 attached fitting 138 with an oil tank 139 connected.
The structural features of the feed pump 126 be regarding the 2 and 4 explained. The delivery pump 126 is essentially the same as the oil return pump 125 , On the outer surface of the crankcase cover 112 is a recess 140 provided as part of the pump housing. The recess 140 freely rotatably supports an outer rotor 141 and an inner rotor 142 , The inner rotor is connected to the pump drive axle 124 firmly connected and stands with the external engine 141 engaged. The outer surfaces of the outer rotor 141 and the inner rotor 142 are with a side cover 113 covered. On the inside of the side cover 113 are an inlet opening 144 and an outlet opening 145 arranged, a working chamber 145 the feed pump 126 face. The inlet opening 144 is through an oil passage 146 and one on the side cover 113 attached fitting 147 with the oil tank 139 connected. The exit opening 145 is one on the inside of the side cover 113 trained oil passage 148 with one in the crankcase cover 112 trained excess reception chamber 149 in connection.
One at the receiving chamber 149 arranged relief valve 150 prevents when the engine is stopped 1 Oil from the oil tank 139 licks. Inside the crankcase cover 112 is a filter chamber 152 with a filter 151 provided therein. The side cover 113 covers the filter insertion hole. The filter chamber 152 and the recording chamber 149 are through an opening 153 connected with each other. The middle area of the filter chamber 152 is over an opening 154 with one inside the side cover 113 trained oil passage 155 connected. The lower end of the oil passage 155 is with the outer circumference of the crank pin 8a over an oil passage 124 passing through the middle of the pump drive shaft 124 runs, and an oil passage 8b passing through the interior of the crankshaft 8th runs, connected. The upper end of the oil passage 155 is with the outer circumference of a camshaft 161 over oil passages 156 . 157 in the crankcase 2 , one around the perimeter of the cylinder block 3 and the cylinder head 4 on the crankcase 2 fixing bolt 158 oil passage formed around 159 and through one inside the cylinder head 4 formed oil passage 160 connected. The on the crankcase 2 trained oil passage 157 is about oil passages 162 and 163 with the circumference of the countershaft 37 of the transmission 36 in connection.
The balancing device described above 7 works as follows. When the crankshaft 8th turns, drives the primary gear 19 the pair of primary balancing weights 22 . 35 at the same speed, but in the opposite direction to the crankshaft 8th at. The pair of secondary balancing weights 44 . 47 is over the drive gear 46 and the idler 49 driven so that both secondary balancing weights 44 . 47 with twice the speed of the crankshaft 8th be rotated, with the first secondary counterweight 44 of the couple in to the crankshaft 8th opposite direction is turned while the second secondary counterweight 47 in the same direction of the crankshaft 8th is turned. In addition, the pair becomes momentum equalizers 50 . 51 over the drive wheel 46 at twice the speed and in the opposite direction of the crankshaft 8th driven.
The result of this damping device is a quieter engine run. The damping of the primary vibrations of the engine are provided by the pair of primary balancing weights 22 . 35 and the secondary vibrations of the engine are through the pair of secondary counterweights 44 . 47 attenuated.
The above components for vibration damping are in the mechanical components of the engine 1 arranged densely packed, by the following geometric relationships between the axle spacings L1, L2 and L3 respectively between the crankshaft 8th and the first first balance shaft 15 , between the crankshaft 8th and the main shaft 16 and between the main shaft 16 and the countershaft 37 when: L1: L2: L3 = 1.5: 1.5: 1
This achieves the following: a short power transmission path, arrangement of all drive components in one plane and compact dimensions of the device, the operating requirements of the two pairs of primary counterweights 22 . 35 and secondary balancing weights 44 . 47 with respect to the operation of the crankshaft.
How out 1 can be seen (dashed circle X), one can by arrangement of the first balance shaft 15 in the front section of the crankcase 2 relative to the cylinder axis above the countershaft 37 of the transmission 36 in the rear section of the crankcase 2 and by arranging the main shaft 16 of the transmission 36 above the crankshaft 8th and the countershaft 37 the position of the lower part of the crankshaft 2 Lower. The use of such a single-cylinder engine in a motorcycle results not only in easier driving over obstacles, but also by lowering the center of gravity safe vehicle characteristics, because the engine 1 can be placed lower in the motorcycle.
When the crankshaft 8th turns, causes the inertia of the balance weight sections 57 . 58 a flywheel effect. At this time, the right balance weight portion moves 58 opposite the wheel 52 smallest diameter at the main shaft 16 of the transmission 36 , so that the moment of inertia of the crankshaft 8th because of increased diameter and thereby increased mass of the right-side balance weight portion 58 is increased.
The effect of torque equalizers 50 . 51 moreover dampens the vibration moment caused by the inertia effect of the combustion and the reciprocating parts of the engine 1 is produced. The vibration of the engine 1 is even more effectively dampened by the fact that one 50 of the pair of moment balancers 50 . 51 on the same axis as the balance weight 44 is arranged to bring the secondary component, which reaches its peak value by the effect of the vibration generated during the combustion process, to zero.
Because beyond that the moment equalizers 50 . 51 from the secondary equalizer 43 . 44 . 47 are separated, one needs the relative positions of the moment balancers 50 . 51 within a certain arc angle of the crankshaft 8th do not set, which is for the engine 1 freer design options arise.
Next, the second balance shaft also serves as the main shaft 16 , The second balance shaft 16 and the third balance shaft 37 fall with each the main shaft 16 and the countershaft 37 of the transmission 36 together. In addition, the torque equalizers 50 . 51 on the first balancer shaft 15 or the main shaft 16 arranged. Due to these design features, no additional waves need to be provided, even if in addition to the primary 22 . 35 and secondary 44 . 47 Compensation devices Torque compensator 50 . 51 are provided, whereby the engine design is simplified.
By the above-described center distances L1, L2, L3, the three gears for the transmission of the secondary balancer and the design conditions for the driven wheel 45 , the intermediate wheel 49 and the driven wheel 48 , all systematized, which improves productivity.
Because the pair of primary balancing weights 22 . 35 outside the crankcase 2 is arranged, it can be easier to determine their arrangement in the crankcase and the point-symmetrical arrangement relative to the center of the crankcase 2 select, which by the first primary balance weight 22 generated force by means of a counterforce of the second primary balance weight 35 can be lifted.
The inventive design therefore allows the damping of the primary vibrations of the engine 1 ,
The operation of the oil pump will be described below. If the crankshaft 8th is rotated, which is at one end of the crankshaft 8th fixed drive shaft 124 turned and through them both the oil return pump 125 as well as the oil pump 126 driven.
By rotation of the outer rotor 128 and the inner rotor 129 the oil return pump 124 the oil passes through the sieve filter 134 filtered and into the oil reservoir 135 sucked. The oil then runs through the oil passage 136 in the crankcase cover 121 and through the inlet opening 132 in the operating chamber 131 the oil pump 125 from which it passes through the outlet 133 is ejected, after which it passes through the oil passage 137 and the connector 138 in the separate oil tank 139 flowing back.
Meanwhile, by action of the outer rotor 141 and the inner rotor 142 the feed pump 126 the oil from the separate oil tank 139 sucked, flows through the connector 147 , the oil passage 146 and through the inlet opening 144 in the operating chamber 143 from where the oil passes through the outlet 145 in the oil passage 148 in the side cover 113 is ejected. The oil then enters the receiving chamber 149 the relief valve 150 where its pressure is set. Then it enters through the opening 153 in the filter chamber 152 of the cylindrical filter 151 where it is filtered from outside to inside in the flow direction of the filter. The filtered oil then passes through an opening 154 in the oil passage 155 in the side cover 113 , Part of the oil will pass after passing the passage 124a in the pump drive axis 124 and the oil passage 8b in the crankshaft 8th the circumference of the crank pin 8a fed. That in the oil passage 155 in the side cover 113 remaining oil flows through the oil passages 156 . 157 . 162 . 163 in the crankcase 2 to the countershaft 37 of the transmission 36 to lubricate. Thereby part of the oil gets from the oil passage 157 branched off to the top after passing the oil passage 159 around the circumference of the bolt 158 and the oil passage 160 in the cylinder head 4 the camshaft 161 to lubricate. The oil that is the parts of the engine 1 is lubricated, is at the bottom of the bottom housing 2 collected and by means of the oil return pump 125 in the oil tank 139 recycled.
The filter can be easily changed because it is removed after removal of the crankcase cover 112 attached side cover 113 through the filter cartridge opening 151 is accessible. That at the oil reservoir 135 of the crankcase 2 provided filter screen 134 can after removal of the crankcase cover 112 from that, crankcase 2 change.
The in the preferred embodiment shown dimensions and arrangements are only examples. There are numerous variants in dependence of the engine type and other design requirements possible.
For example, the left-side balance weight portion 57 thicker than the right balance weight section 58 be formed. The thickness of both weights can also be the same.
The oil return pump 125 is on the inner surface of the crankcase cover 112 and the booster pump 126 arranged on its outside. However, the arrangement of these two pumps 125 and 126 also be the other way around. The pumps 125 and 126 are trochiod pumps in the examples shown. However, other types of pumps, such as internal gear teeth with internal teeth and external teeth, or external gear pumps with two external gear teeth may also be used.
The invention relates to an improved system for dynamically balancing combustion and inertial torque effects of associated primary and secondary vibrations, especially of single-cylinder engines. First and second balancer shafts provide the best balancing effects achieved by combining power transmission and dynamic balancing functions of the waves, by arranging the first and second balancer shafts near and parallel to the crankshaft and by a judicious choice of the center distances, which can be attached to the compensation parts maximum torque compensation weights.
Drive device for a motor vehicle with a motor ( 1 ), a crankshaft ( 8th ) and a transmission ( 36 ), the apparatus comprising: (a) a pair having the same rotational speed of the crankshaft ( 8th ) rotating primary balance weights ( 22 . 35 ) and a pair of double speed crankshaft ( 8th ) rotating secondary balance weights ( 44 . 47 ), (b) a first balance shaft ( 15 ) and a second balance shaft ( 16 ), both close and parallel to the crankshaft ( 8th ), the first ( 15 ) and the second ( 16 ) Balance shaft from the crankshaft by means of gears ( 19 . 26 . 34 ) are driven, wherein at the first balancer shaft ( 15 ) two balance weights ( 22 ; 44 ), namely one each ( 22 ; 44 ) of the pairs of primary and secondary balancing weights ( 22 . 35 ; 44 . 47 ), and wherein the one remaining balance weight ( 35 ) of the pair of primary balancing weights ( 22 . 35 ) on the second balance shaft ( 16 ), and (c) a close and parallel to the second balance shaft (FIG. 16 ), of the second balance shaft ( 16 ) via gears ( 46 . 49 . 48 ) driven third balance shaft ( 37 ), the remaining balance weight ( 47 ) of the pair of secondary balancing weights ( 44 . 47 ) on the third balance shaft ( 37 ), wherein the positional relationships of the components are: L1: L2: L3 = 1.5: 1.5: 1 where the symbols L1, L2 and L3 denote the distances between the components as follows: L1 the center distance between the first balance shaft ( 15 ) and the crankshaft ( 8th ), L2 the center distance between the crankshaft ( 8th ) and the second balance shaft ( 16 ) and L3 the center distance between the second balance shaft ( 16 ) and the third balance shaft ( 37 ), characterized in that respective power transmission systems ( 19 . 26 . 34 ; 46 . 50 51 . 48 ) for the primary and secondary balancing weights ( 22 . 35 ; 44 . 47 ) are arranged in each case in a common plane.
Drive device according to claim 1, characterized in that the second balance shaft, the main shaft ( 16 ) of the transmission ( 36 ).
Drive device according to claim 1 or 2, characterized in that the third balance shaft, the counter shaft ( 37 ) of the transmission ( 36 ).
Drive device for a motor vehicle with a motor ( 1 ), a crankshaft ( 8th ) and a transmission ( 36 ), in particular according to one of the preceding claims, the device comprising: (a) a close and parallel to the crankshaft ( 8th ) arranged balance shaft ( 15 ) with a first driven gear wheel ( 26 ) and one around the balance shaft ( 15 ) rotatable second driven gear ( 45 ), (b) a primary gear ( 19 ) and a drive wheel ( 46 ) on the crankshaft ( 8th ) are arranged, wherein the primary gear ( 19 ) for transmitting driving force to the balance shaft ( 15 ), with the first driven gear ( 26 ), and the drive wheel ( 46 ) with the second driven gear ( 45 ) is engaged, (c) one on the balance shaft ( 15 ), dampening rotational engine vibrations during primary balancing weight ( 22 ), and (d) a gear driven by the second gear ( 45 ) one-piece secondary balancing weight damping during rotation engine vibrations ( 44 ), characterized in that the mass of the second driven gear ( 45 ) is distributed in the radial direction such that it has a moment compensator ( 50 ) for damping engine vibrations, wherein the torque compensator ( 50 ) integral with the driven gear ( 45 ) is designed such that the torque equalizer ( 50 ) of the driven gear ( 45 ) protrudes in its axial direction.
Drive device according to claim 4, characterized in that the thickness of the second driven gear ( 45 ) is non-uniform.
Drive device according to claim 4 or 5, characterized in that the second driven gear ( 45 ) the secondary balance weight ( 44 ) and at twice the speed of the crankshaft ( 8th ) turns to secondary vibrations of the engine ( 1 ) to dampen.
Drive device according to one of claims 4 to 6, characterized in that the local mass distribution of the second driven gear ( 45 ) out of phase with the secondary counterweight ( 44 ).
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JP28015290A JP3071815B2 (en) 1990-10-18 1990-10-18 Engine balancer device
DE4134399A1 DE4134399A1 (en) 1992-04-23
DE4134399B4 true DE4134399B4 (en) 2006-08-10
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