CN201293066Y - All balance mechanism for single cylinder diesel - Google Patents
All balance mechanism for single cylinder diesel Download PDFInfo
- Publication number
- CN201293066Y CN201293066Y CNU2008201619555U CN200820161955U CN201293066Y CN 201293066 Y CN201293066 Y CN 201293066Y CN U2008201619555 U CNU2008201619555 U CN U2008201619555U CN 200820161955 U CN200820161955 U CN 200820161955U CN 201293066 Y CN201293066 Y CN 201293066Y
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- slide block
- cambered surface
- annular connecting
- backward
- connecting rod
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Abstract
The utility model relates to a full-balance mechanism of a single-cylinder diesel engine, which comprises a crank, a front circular link, a rear circular link, a front slide block, a rear slide block and a guide component, wherein the crank is provided with a front eccentric neck journal and a rear eccentric neck journal, and the front circular link and the rear circular link are respectively mounted at the front eccentric neck journal and the rear eccentric neck journal by a front bearing and a rear bearing and respectively arranged in the left guide arc surface and the right guide arc surface of the front slide block and the rear slide block; a front guide pin and a rear guide pin of the guide component are respectively arranged in guide grooves of the front slide block and the rear slide block, a front guide rod and a rear guide rod respectively penetrate guide holes of the front slide block and the rear slide block and are connected with support shafts, and a ratio of the eccentric distance e between the eccentric neck journals to the working length 1 of the circular links is equal to a ratio of the radius R of the crank to the working length L of the circular links. The utility model can fully balance the first-order reciprocating inertia force and the second-order reciprocating inertia force of the single-cylinder diesel engine and can reduce the vibration and the noise of the diesel engine.
Description
Technical field
The utility model relates to the full balanced controls of a kind of single cylinder diesel, belongs to the balancing technique field of single cylinder diesel.
Background technique
Greatly, middle-size and small-size single cylinder diesel mainly is made of body part, crankshaft ﹠ connecting, air exchange system, fuel supply system etc., by rotatablely moving of the piston to-and-fro motion in cylinder becoming bent axle, again rotatablely moving of bent axle become the to-and-fro motion of piston, to realize work cycle and external outputting power and each the auxiliary system work that is used for driving motor.Because the pairing linkage mechanism of cylinder all can produce a reciprocal inertia force and rotating inertia force, and the moment of inertia that these two inertial force are also formed two kinds of alternations affacts on the main bearing, these inertial force and moment are not only to diesel engine itself and very unfavorable to the work of outfitting tool, especially for single cylinder diesel because of having only a cylinder, inertial force that can not self balance diesel engine connecting rod is so need to add the equilibrium problem that extra balanced controls solve connecting rod.At present, the balanced controls that generally adopt of single-cylinder horizontal diesel engine have excessive balance mechanism, uniaxiality balance Agency And spindle balance mechanism.
Excessive balance mechanism adds certain balancing mass on crankshaft balance weight, make bent axle produce excessive inertial force, a part is transferred to Vertical direction along the reciprocal inertia force of cylinder centerline, thereby make single order reciprocal inertia force peak value descend to some extent.
Uniaxiality balance mechanism adds the balancer weight except be positioned at the opposite side of crank pin at bent axle, trunnion shaft of gear driven by the bent axle axle head rotates with unequal angular velocity again, the rotating inertia force that utilizes two balancer weights comes the balance reciprocal inertia force along the component of cylinder-bore axis, and their component perpendicular to cylinder-bore axis is cancelled each other, but because this two power is not point-blank, also can produce unbalanced moment, therefore can only balance part reciprocal inertia force.
Double-shaft balance mechanism adopts two trunnion shafves that two sense of rotation are opposite, size is identical, the centrifugal force of two trunnion shafves reaches balance along the component of cylinder centerline direction and the single order reciprocal inertia force of piston set, but mechanism element quantity is many, and volume and weight is big, the cost height.
Though above-mentioned balanced controls can solve the rotatory inertia equilibrium of forces of connecting rod substantially, but can only partly or entirely balance the single order reciprocal inertia force, all can not solve the equilibrium problem of two-stage reciprocating inertia force, and two-stage reciprocating inertia force is about 1/3～1/4 of single order reciprocal inertia force, so the balanced controls of present single cylinder diesel are because can't the complete equilibrium reciprocal inertia force, be to cause the big main cause of single cylinder diesel ubiquity vibration and noise, both cause noise circumstance to pollute, had a strong impact on user's travelling comfort again.
Summary of the invention
The purpose of this utility model provides a kind of single order and two-stage reciprocating inertia force of energy balance diesel engine, can reduce the full balanced controls of single cylinder diesel of diesel vibration and noise.
The utility model is that the technological scheme that achieves the above object is: the full balanced controls of a kind of single cylinder diesel is characterized in that: comprise bent axle, fore bearing, rear bearing, preceding annular connecting rod, the annular connecting rod in back, front-slider, rear slider and guidance set; Be arranged with the axle center between described crankshaft crank both sides and the forward and backward main journal and be in reverse to forward and backward two eccentric journals of crank pin one side; Described structure shape identical before, the outer circumferential face of back two annular connecting rods is by the left cambered surface of two ends concentric, right cambered surface and transition cambered surface constitute, the right cambered surface radius R1 that is in reverse to crank pin one side is less than left cambered surface radius R2, a left side, the center of circle of right cambered surface is to bent axle, the distance in two eccentric journal axle center, back is annular connecting rod active length l, before, before back two annular connecting rods are set in, on the back two bearings and before bent axle is installed, two eccentric journal places, back, before, the back two annular connecting rods be installed in respectively structure shape identical before, in the left curved guiding surface and right curved guiding surface of back two slide blocks, before, the back two slide blocks left curved guiding surface with before, the left cambered surface radius R2 of back two annular connecting rods equates, and left curved guiding surface arc length is greater than left cambered surface arc length, before, the back two slide blocks right curved guiding surface with before, the right cambered surface radius R1 of back two annular connecting rods equates, and right curved guiding surface arc length is less than right cambered surface arc length; Described guidance set comprises forward and backward two guide fingers that are installed in the body top and forward and backward two guide rods and the back shaft that is installed in underpart, forward and backward two guide fingers are separately positioned in the guiding groove of forward and backward two slider top, and the pilot hole that forward and backward two guide rods pass forward and backward two slide block bottoms respectively is connected with back shaft.
Wherein, the eccentric distance e of described forward and backward two eccentric journals and forward and backward two annular connecting rod active length l ratios equal the ratio of throw of crank shaft R and connecting rod active length L.
The utility model is because with the crank radius of the throw of eccentric between eccentric journal and the main journal as balanced controls, and before being installed in, before on two eccentric journals of back, the two ends cambered surface of back two annular connecting rods is concentric and different right cambered surface and the left cambered surfaces of radius, this right side cambered surface and left cambered surface are served as the microcephaly and the major part of annular connecting rod respectively, and with preceding, the right side of back two slide blocks, left side curved guiding surface matches, when bent axle rotates, before, before back two eccentric journals pass through, before back two bearings drives, back two annular connecting rods are done plane turn swing, before then driving, back two slide blocks do reciprocating linear motion in the cylinder centerline direction, before making, the to-and-fro motion track of back two slide blocks and the movement locus conllinear of piston, and moving direction is opposite, forms similar opposed two connecting rods.The utility model is because the ratio of the eccentric distance e of forward and backward two eccentric journals and forward and backward two annular connecting rod active length l equals the ratio of throw of crank shaft R and connecting rod active length L, rotating inertia force that promptly can the complete equilibrium bent axle, can offset with the reciprocal inertia force that piston produces again, reach the complete equilibrium of single order and two-stage reciprocating inertia force.Balance method of the present utility model and mechanism are owing to energy complete equilibrium single order and two-stage reciprocating inertia force, so reduced the diesel vibration and the noise of single cylinder diesel.In addition, the utility model is because these balanced controls have been cancelled trunnion shaft, and do not change structures such as piston, connecting rod, eccentric journal and connected annular connecting rod and slide block only on the bent axle basis, have been increased, and body improved, structural arrangements is more reasonable, compact, takies the body space and reduces, and can further shorten the length of diesel-engine body.
Description of drawings
Below in conjunction with accompanying drawing embodiment of the present utility model is described in further detail.
Fig. 1 is the blast structural representation of the full balanced controls of the utility model single cylinder diesel.
Fig. 2 is the perspective view of the utility model bent axle.
Fig. 3 is the structural representation of piston, connecting rod, the bent axle after the utility model splits, preceding annular connecting rod, front-slider.
Fig. 4 is that the full balanced controls of model utility are installed in the structural representation in the body.
Fig. 5 is the A-A sectional structure schematic representation of Fig. 4.
Wherein: 1-piston, 2-wrist pin, 3-connecting rod, 4-bent axle, 4-1-forward spindle neck, 4-2-pre-eccentric axle journal, 4-3-crank, 4-4-crank pin, eccentric journal behind the 4-5-, main journal behind the 4-6-, 5-front-slider, the left front slide block of 5-1-, the right front slide block of 5-2-, 5-3-guiding groove, 5-4-pilot hole, 5-5-left side curved guiding surface, the right curved guiding surface of 5-6-, annular connecting rod before the 6-, the right cambered surface of 6-1-, 6-2-left side cambered surface, 6-3-transition cambered surface, guide finger before the 7-, the 8-fore bearing, the last bolt of 9-, bolt under the 10-, the 11-rear slider, the left back slide block of 11-1-, the right back slide block of 11-2-, the 11-3-guiding groove, 11-4-left side curved guiding surface, the right curved guiding surface of 11-5-, annular connecting rod behind the 12-, the right cambered surface of 12-1-, 12-2-left side cambered surface, the 13-rear bearing, guide rod before the guide finger behind the 14-, 15-, guide rod behind the 16-, 17-back shaft, 18-body.
Embodiment
See shown in Fig. 1～5, the full balanced controls of single cylinder diesel of the present utility model comprise bent axle 4, fore bearing 8, rear bearing 13, preceding annular connecting rod 6, the annular connecting rod 12 in back, front-slider 5, rear slider 11 and guidance set, the major part of connecting rod 3 is connected with crank 4-3, and the microcephaly of connecting rod 3 is connected with piston 1 by wrist pin 2.See Fig. 2, shown in 3, the crank 4-3 both sides of the utility model bent axle 4 respectively and be arranged with pre-eccentric axle journal 4-2 and back eccentric journal 4-5 between forward spindle neck 4-1 and the back main journal 4-6, the axle center of pre-eccentric axle journal 4-2 and back eccentric journal 4-5 is opposite with crank pin 4-4 direction, eccentric distance e between the axle center of the axle center of pre-eccentric axle journal 4-2 and back eccentric journal 4-5 and forward spindle neck 4-1 and back main journal 4-6, be the turning radius of eccentric journal around crankshaft axis, this eccentric distance e is as the crank radius of balanced controls, make the balancer weight of the quality of the eccentric journal on the bent axle 4 as bent axle, to reduce the quality of bent axle, see shown in Figure 3, the footstalk radius of bent axle 4 is R, L is a length of connecting rod, and the radius of pre-eccentric axle journal 4-2 and back eccentric journal 4-5 is R3.
See shown in Fig. 1,3,4, annular connecting rod 12 structure shapes of annular connecting rod 6 and back are identical before of the present utility model, the outer circumferential face of preceding annular connecting rod 6 is made of two ends concentric and different right cambered surface 6-1, left cambered surface 6-2 and the two symmetrical transition cambered surface 6-3 of radius, the right cambered surface 6-1 radius R 1 of preceding annular connecting rod 6 is less than left cambered surface 6-2 radius R 2, the right cambered surface 6-1 of preceding annular connecting rod 6 is opposite with the crank pin direction, and the distance between the right cambered surface 6-1 of preceding annular connecting rod 6 and the center of circle of left cambered surface 6-2 to the bent axle 4 pre-eccentric axle journal 4-2 axle center is annular connecting rod active length l.See Fig. 1, shown in 5, equally, the outer circumferential face of the annular connecting rod 12 in back is also by two ends concentric and the different right cambered surface 12-1 of radius, two transition cambered surfaces of left side cambered surface 12-2 and symmetry constitute, the right cambered surface 12-1 radius R 1 of the annular connecting rod 12 in back is less than left cambered surface 12-2 radius R 2, the right cambered surface 12-1 of the annular connecting rod 12 in back is opposite with the crank pin direction, distance is annular connecting rod active length l between the right cambered surface 12-1 of the annular connecting rod 12 in back and the center of circle to the back eccentric journal 4-5 axle center of bent axle 4 of left cambered surface 12-2, before making the right cambered surface 12-1 of the annular connecting rod 12 of the right cambered surface 6-1 of annular connecting rod 6 and left cambered surface 6-2 and back and left cambered surface 12-2 as the major part of two annular connecting rods and microcephaly respectively with the left side of front-slider 5, the left side of right curved guiding surface and rear slider 11, right curved guiding surface cooperates, to form opposed two connecting rods, the movement locus conllinear of its movement locus and piston, and direction is opposite.See shown in Fig. 1,5, the annular connecting rod 12 of annular connecting rod 6 and back is set on fore bearing 8 and the rear bearing 13 and is installed on the pre-eccentric axle journal 4-2 and back eccentric journal 4-5 of bent axle 4 before of the present utility model, and preceding annular connecting rod 6 and the annular connecting rod 12 in back are installed in respectively in the left and right curved guiding surface of the left and right curved guiding surface of front-slider 5 and rear slider 11.
See shown in Fig. 1,3,4,5, front-slider 5 of the present utility model is identical with rear slider 11 structure shapes, front-slider 5 has left curved guiding surface 5-5 and right curved guiding surface 5-6, top have guiding groove 5-3, equally, rear slider 11 also has left curved guiding surface 11-4 and right curved guiding surface 11-5, top have guiding groove 11-3, the bottom of front-slider 5 also has pilot hole 5-4, and the bottom of rear slider 11 also has pilot hole.For ease of installing and control, front-slider 5 is made of left front slide block 5-1 and right front slide block 5-2, on left front slide block 5-1 has, following two tapped holes, and right front slide block 5-2 have corresponding on, following two unthreaded holes, last bolt 9 and following bolt 10 pass respectively right front slide block 5-2 on, following two unthreaded holes and be screwed in left front slide block 5-1 on, in following two tapped holes, left front slide block 5-1 is connected with right front slide block 5-2, the right curved guiding surface 5-6 radius of right front slide block 5-2 equates with preceding annular connecting rod 6 right cambered surface 6-1 radius Rs 1, and the right curved guiding surface 5-6 arc length of right front slide block 5-2 is less than the right cambered surface 6-1 arc length of preceding annular connecting rod 6, and the left curved guiding surface 5-5 radius of left front slide block 5-1 equates with preceding annular connecting rod 6 left cambered surface 6-2 radius Rs 2, the left curved guiding surface 5-5 arc length of left front slide block 5-1 is greater than preceding annular connecting rod 6 left cambered surface 6-2 arc length, under the drive of bent axle 4, the right cambered surface 6-1 of annular connecting rod 6 and left cambered surface 6-2 do the plane rotary oscillation before making in the right curved guiding surface 5-6 of front-slider 5 and left curved guiding surface 5-5.See Fig. 1 equally, shown in 4, rear slider 11 of the present utility model also is made of left back slide block 11-1 and right back slide block 11-2, last bolt 9 is connected left back slide block 11-1 with following bolt 10 with right back slide block 11-2, the right curved guiding surface 11-5 radius of right back slide block 11-2 equates with the right cambered surface 12-1 radius R 1 of the annular connecting rod 12 in back, the right curved guiding surface 11-5 arc length of right back slide block 11-2 is less than the right cambered surface 12-1 arc length of the annular connecting rod 12 in back, the left curved guiding surface 11-4 radius of left back slide block 11-1 equates with the annular connecting rod 12 left cambered surface 12-2 radius Rs 2 in back, the left curved guiding surface 11-4 arc length of left back slide block 11-1 is greater than the annular connecting rod 12 left cambered surface 12-2 arc length in back, equally, back right cambered surface 12-1 of annular connecting rod 12 and left cambered surface 12-2 do the plane rotary oscillation in the right curved guiding surface 11-5 of rear slider 11 and left curved guiding surface 11-4.
See Fig. 1,4, shown in 5, guidance set of the present utility model comprises the preceding guide finger 7 that is installed in body 18 tops and back guide finger 14 and the preceding guide rod 15 that is installed in body 18 bottoms, back guide rod 16 and back shaft 17, before guide finger 7 and back guide finger 14 be separately positioned in the guiding groove 11-3 of the guiding groove 5-3 of front-slider 5 and rear slider 11, make front-slider 5 and rear slider 11 when reciprocating, play position-limiting action, preceding guide rod 15 and back guide rod 16 pass the pilot hole 5-4 of front-slider 5 bottoms and the pilot hole of rear slider 11 bottoms respectively, and preceding guide rod 15 is connected with back shaft 17 with back guide rod 16, the hole that preceding guide rod 15 of two installations and back guide rod 16 are arranged on this back shaft 17, and the tapped hole of two correspondences arranged on the Vertical direction in two holes, and be fixed by bolts on preceding guide rod 15 and the back guide rod 16, by the guiding of pilot hole, before making, back two slide blocks 5 and 11 move reciprocatingly in body 18.
Before of the present utility model, the ratio of eccentric distance e and the front and back two annular connecting rod active length l of back two eccentric journals equals the ratio of throw of crank shaft R and connecting rod active length L, owing to can form opposed two connecting rods, before, back two slide blocks 5 and 11 movement locus and the movement locus conllinear of piston 1, moving direction is opposite, by the suitable eccentric distance e of control balanced controls, annular connecting rod active length l, the moving-mass of bent axle 4 and slide block, both can the complete equilibrium rotating inertia force, simultaneously, back two slide blocks 5 and 11 reciprocal inertia forces that produce can offset with the reciprocal inertia force that piston 1 produces again, reach the complete equilibrium of single order and two-stage reciprocating inertia force.
Claims (4)
1, the full balanced controls of a kind of single cylinder diesel is characterized in that: comprise bent axle, fore bearing, rear bearing, preceding annular connecting rod, the annular connecting rod in back, front-slider, rear slider and guidance set; Be arranged with the axle center between described crankshaft crank both sides and the forward and backward main journal and be in reverse to forward and backward two eccentric journals of crank pin one side; Described structure shape identical before, the outer circumferential face of back two annular connecting rods is by the left cambered surface of two ends concentric, right cambered surface and transition cambered surface constitute, the right cambered surface radius R1 that is in reverse to crank pin one side is less than left cambered surface radius R2, a left side, the center of circle of right cambered surface is to bent axle, the distance in two eccentric journal axle center, back is annular connecting rod active length l, before, before back two annular connecting rods are set in, on the back two bearings and before bent axle is installed, two eccentric journal places, back, before, the back two annular connecting rods be installed in respectively structure shape identical before, in the left curved guiding surface and right curved guiding surface of back two slide blocks, before, the back two slide blocks left curved guiding surface with before, the left cambered surface radius R2 of back two annular connecting rods equates, and left curved guiding surface arc length is greater than left cambered surface arc length, before, the back two slide blocks right curved guiding surface with before, the right cambered surface radius R1 of back two annular connecting rods equates, and right curved guiding surface arc length is less than right cambered surface arc length; Described guidance set comprises forward and backward two guide fingers that are installed in the body top and forward and backward two guide rods and the back shaft that is installed in underpart, forward and backward two guide fingers are separately positioned in the guiding groove of forward and backward two slider top, and the pilot hole that forward and backward two guide rods pass forward and backward two slide block bottoms respectively is connected with back shaft.
2, the full balanced controls of single cylinder diesel according to claim 1 is characterized in that: the eccentric distance e of described forward and backward two eccentric journals and forward and backward two annular connecting rod active length l ratios equal the ratio of throw of crank shaft R and connecting rod active length L.
3, the full balanced controls of single cylinder diesel according to claim 1 is characterized in that: described front-slider is made of left front slide block and right front slide block, and upper and lower two bolts are connected left front slide block with right front slide block.
4, the full balanced controls of single cylinder diesel according to claim 1 is characterized in that: described rear slider is made of left back slide block and right back slide block, and upper and lower two bolts are connected left back slide block with right back slide block.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201619555U CN201293066Y (en) | 2008-10-24 | 2008-10-24 | All balance mechanism for single cylinder diesel |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201619555U CN201293066Y (en) | 2008-10-24 | 2008-10-24 | All balance mechanism for single cylinder diesel |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201293066Y true CN201293066Y (en) | 2009-08-19 |
Family
ID=41006543
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008201619555U Expired - Lifetime CN201293066Y (en) | 2008-10-24 | 2008-10-24 | All balance mechanism for single cylinder diesel |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201293066Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102322473A (en) * | 2011-05-24 | 2012-01-18 | 金坛鑫田柴油机有限公司 | Single cylinder diesel convenient for direct connection driving |
| WO2019233200A1 (en) * | 2018-06-07 | 2019-12-12 | 重庆宗申通用动力机械有限公司 | Engine balance system |
-
2008
- 2008-10-24 CN CNU2008201619555U patent/CN201293066Y/en not_active Expired - Lifetime
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102322473A (en) * | 2011-05-24 | 2012-01-18 | 金坛鑫田柴油机有限公司 | Single cylinder diesel convenient for direct connection driving |
| CN102322473B (en) * | 2011-05-24 | 2016-06-08 | 江苏鑫田柴油机有限公司 | A kind of one-cylinder diesel machine be convenient to straight connection and drive |
| WO2019233200A1 (en) * | 2018-06-07 | 2019-12-12 | 重庆宗申通用动力机械有限公司 | Engine balance system |
| EP3805599A4 (en) * | 2018-06-07 | 2021-08-25 | Chongqing Zongshen General Power Machine Co., Ltd. | Engine balance system |
| US11466615B2 (en) | 2018-06-07 | 2022-10-11 | Chongqing Zongshen General Power Machine Co., Ltd. | Engine balancing system |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20090819 Effective date of abandoning: 20081024 |