CN86108669A - Multicylinder conjugate diesel engine with capless double-piston cylinders - Google Patents
Multicylinder conjugate diesel engine with capless double-piston cylinders Download PDFInfo
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- CN86108669A CN86108669A CN86108669.4A CN86108669A CN86108669A CN 86108669 A CN86108669 A CN 86108669A CN 86108669 A CN86108669 A CN 86108669A CN 86108669 A CN86108669 A CN 86108669A
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Abstract
Multicylinder conjugate diesel engine with capless double-piston cylinders belongs to piston reciprocating internal combustion engine.The present invention designs a kind of at least four cylinders and is arranged in parallel, two heterodromous each other pistons are housed in each cylinder, the inlet and outlet door is installed on the two-piston respectively, in each cylinder, surround the firing chamber by cylinder liner and two pistons, each piston of cylinder two ends homonymy is by the fixedly connected tranverse connecting rod of piston rod, and the two-end part of tranverse connecting rod is positioned in the guide rail, and power take-off mechanism and the distribution device that transmits piston motion arranged.The present invention can symmetry utilize the combustion gas expansive force, and improves combustion condition and adopt high compression ratio, eliminates the side pressure of piston to working cylinder.
Description
The invention belongs to piston reciprocating internal combustion engine.
At present, the piston reciprocating type diesel engine is formed working cylinder by cylinder block, cylinder liner and cylinder head, and piston is reciprocating therein, and the combustion gas folk prescription is to promoting the piston work done.Inlet and outlet door and oil nozzle all are arranged on the cylinder cap.Transmit piston motion and output cylinder output in connecting rod drive bent axle mode.Now organically these features make motive power be difficult for realizing good balance, so that produce vibrations and noise; Air inlet, exhaust all are restricted, and are difficult to adopt high compression ratio, so also just are difficult to further improve the thermal efficiency.Existing machine makes and further strengthens strength of vortex, improves empty combustion mixing rate and is restricted.Because piston is bigger to the side pressure of cylinder sleeve, increased the wearing and tearing and the mechanical loss of cylinder sleeve.
The present invention designs a kind of energy symmetry utilize the combustion gas expansive force, and improves combustion condition and adopt high compression ratio, eliminates the multicylinder conjugate diesel engine with capless double-piston cylinders of piston to the side pressure of working cylinder.
To achieve these goals, the present invention designs a kind of at least four cylinders and is arranged in parallel, two heterodromous each other pistons are housed in each cylinder, the inlet and outlet door is installed on the two-piston respectively, in each cylinder, surround the firing chamber by cylinder liner and two pistons, each piston of cylinder two ends homonymy is by the fixedly connected tranverse connecting rod of piston rod, the two-end part of tranverse connecting rod is positioned in the guide rail, and power take-off mechanism and the distribution device that transmits piston motion arranged.
Below in conjunction with accompanying drawing the present invention is done detailed description.
Fig. 1 is a plan view of the present invention
Fig. 2 is a piston B-B sectional drawing
Fig. 3 is a piston C-C sectional drawing
Fig. 4 is a piston D-D sectional drawing
Fig. 5 is secondary crankshaft and main crankshaft connection diagram
Fig. 6 is secondary crankshaft and main shaft connection diagram
Fig. 7 is the distribution device left view
Fig. 8 is air inlet control principle figure
Fig. 9 is exhaust control principle figure
Figure 10 is the polynary conjugation-type diesel engine of an one deck layout viewing
Figure 11 is two layers of unit conjugation-type diesel engine layout viewing
Figure 12 is two layers of unit conjugation-type diesel engine vertical links figure
Main diagrammatic sketch of the present invention as shown in Figure 1.At least four cylinders are arranged in parallel, in each cylinder (1) lining two heterodromous each other pistons (2,2 ') are housed, the inlet and outlet door is installed on the two-piston respectively, in each cylinder (1) lining, surround the firing chamber by cylinder liner and two pistons (2,2 '), each piston of cylinder two ends homonymy (2,2 ') is by the fixedly connected tranverse connecting rod of piston rod (7,7 ') (10,10 '), the two-end part of tranverse connecting rod is positioned in the guide rail, and power take-off mechanism and the distribution device that transmits piston motion arranged.Cylinder liner can be contained in forms cylinder on the cylinder block, the oil nozzle 11 of each cylinder (1) is positioned on the centre of cylinder, forms the centre of the firing chamber of each cylinder at two-piston.Guide rail can be positioned on the body, has two guide rails to support tranverse connecting rod at the tranverse connecting rod two-end part, shown in the A-A sectional drawing.
Structure of piston such as Fig. 1, Fig. 2, Fig. 3, shown in Figure 4.Piston 2 is made up of piston sleeve 3, piston cylinder 4 and piston rod 7, and the axis part of piston has gas-entered passageway, and is equipped with valve stem 5 and swirl vane 6 in passage; The inner vortex of swirl vane is wrapped on the bar of valve stem 5, outer vortex and gas-entered passageway inner hole surface close contact.Piston 2 ' by piston sleeve 3 ', piston cylinder 4 ' and piston rod 7 ' form, the axis part of piston has the exhaust passage, and in passage, be equipped with valve stem 5 '.Piston 2 ' roughly the same with the structure of piston 2 is not just pacified swirl vane.Its axis part of piston cylinder has endoporus, as the inlet and outlet passage, supporting member (8,8 ') is arranged in endoporus, supporting valve stem (5,5 ').Cut two on the top of piston cylinder, form piston rod (7,7 ').One end of valve stem is made bacterium shape air valve, and the male cone (strobilus masculinus) of bacterium shape air valve cooperates closely with the inner conical surface of piston inner hole piston side.On the supporting member (8,8 ') of upper end, be fixed with spring (9,9 ') tension valve stem (5,5 ').When the oil gas of firing chamber burns, promote two pistons simultaneously and move the propulsion power output mechanism outward.After the cylinder work done finishes, by the inertia of power take-off mechanism, drive piston simultaneously to the motion of cylinder middle part, this moment valve stem 5 ' backed down the cylinder exhaust by distribution device.When exhaust finishes, piston is simultaneously to the outer end motion of cylinder, and this moment, valve stem 5 was backed down by distribution device, and cylinder is air-breathing, and air is by forming the eddy current along the cylinder cross-sectional periphery, to improve empty combustion mixing rate behind the swirl vane.Piston is simultaneously to cylinder middle part motion compresses air, for work done is next time prepared then.
Power take-off mechanism such as Fig. 1, Fig. 5, shown in Figure 6.It is formed by be positioned on tranverse connecting rod (10,10 ') in the guide rail, connecting rod (12,12 ', 13,13 ') and the secondary crankshaft (14,14 ') of four cylinder both sides at the cylinder two ends at least.
The piston that gas-entered passageway is arranged of at least four cylinders is positioned on the same side of cylinder.Tranverse connecting rod (10,10 ') is the piston rod of fixedly connected at least four its homonymies of cylinder respectively.The upper end of the piston rod of each cylinder (7,7 ') is recessed, forms boss, and push up mutually with tranverse connecting rod at the boss place, fixedlys connected with tranverse connecting rod at recessed section piston rod.The two ends of tranverse connecting rod (10,10 ') are hinged with an end of connecting rod (12,12 ', 13,13 ') respectively, the other end of connecting rod is hinged on the secondary crankshaft (14,14 ') at cylinder two ends, form connecting rod 12 and 12 ', connecting rod 13 and 13 ' opposed tranverse connecting rod (10,10 ') and the secondary crankshaft (14,14 ') of being connected.When combustion gas promoted the two-way work done of two-piston, piston promoted tranverse connecting rod and do translation in guide rail, and the tranverse connecting rod of translation drives the rotation of opposed connecting rod pulling secondary crankshaft.
Secondary crankshaft drives pto and rotatablely moves as Fig. 5, shown in Figure 6.Secondary crankshaft (14,14 ') can pass through vertical links (17,17 ', 18,18 ', 19,19 ') connect main crankshaft 15.One end of vertical links 17,18,19 is hinged on the crank throw 22,23,24 of secondary crankshaft 14, the other end of vertical links 17,18,19 be hinged on the crank throw 26,25,24 of main crankshaft 15 ' on.The crank 28,29 that links to each other with crank throw 23,24 differs 180 °.The crank 27 and the crank 28 that link to each other with crank throw 24 differ certain angle, and this angle is greater than 0 °, less than 180 °.In the time of can making the secondary crankshaft rotation like this, the drive main crankshaft is crossed stop and is moved in the same way.Secondary crankshaft 14 ' by vertical links 17 ', 18 ', 19 ' connect, the arrangement that vertical links connects the mode of major and minor bent axle and crank is identical with the mode of secondary crankshaft 14.
Secondary crankshaft also can mesh gear on the main shaft 16 by train of gearings, and secondary crankshaft (14,14 ') is by 16 rotations of gear driven main shaft.Secondary crankshaft (14,14 ') be equipped with timing gear (30,30 ') can with the gear engagement on the main shaft.By main crankshaft 15 or main shaft 16 outputting powers.
When the cylinder combustion gas promotes the two-piston work done, tranverse connecting rod (10,10 ') is motion outward simultaneously, and tranverse connecting rod is done translation in guide rail, and its drivening rod (12,12 ', 13,13 ') draws secondary crankshaft to rotatablely move.Secondary crankshaft can drive main crankshaft by vertical links and rotatablely move, and also can drive the main axis rotation motion by train of gearings.When lower dead center is arrived in piston motion, because there are two flywheels at main crankshaft or main shaft two ends, rely on inertia to make secondary crankshaft continue motion, continue to do other stroke by tranverse connecting rod help piston.
Distribution device such as Fig. 1, shown in Figure 7.It is made up of the depression bar (37,37 ') that is installed in timing gear (31,31 ') on the axis 32 and cam (33,33 ') and tooth sector (34,34 '), crank gear (35,35 '), two slidercrank mechanisms, is equipped with briquetting (36,36 ').
By tooth sector 34, cam 33, crank gear 35, slidercrank mechanism (38,39,40), depression bar 37 with fixedly be positioned on valve top 41 control air inlets actions on the slide block 40.By tooth sector 34 ', cam 33 ', crank gear 35 ', slidercrank mechanism (38 ', 39 ', 40 '), depression bar 37 ' and fixedly be positioned on slide block 40 ' on valve top 41 ' control exhaust action.
The two ends of axis 32 fixedly are equipped with timing gear (31,31 '), the timing gear (30,30 ') on timing gear (31,31 ') the engagement pair bent axles (14,14 ').Secondary crankshaft then drives the rotation of axis 32.Be installed with tooth sector 34 at axis 32, its half cycle is anodontia, and its half cycle has tooth position engagement crank gear 35.Fixedly be equipped with crank 38 on crank gear 35, it is along with crank gear 35 rotates, drivening rod 39, and connecting rod 39 drives the slide block 40 that moves in guide rail, and then valve top 41 rotations along with crank gear are along valve stem 5 axial location to-and-fro motion.When tooth sector 34 half cycles have tooth position and crank gear to begin to mesh, cam jack-up depression bar 37, have tooth pressure piece 36 and crank gear 35 on the depression bar 37 are thrown off, and crank gear 35 is with tooth sector 34 rotations.When tooth position engagement finished, depression bar was reduced to low spot by the height point of cam 33 under the effect of spring 42, and briquetting 36 and crank gear 35 pressings, crank gear 35 are located not rotary valve top 41 and also just not moved.
The number of teeth of selecting timing gear (31,31 ') is two times of timing gear (30, the 30 ') number of teeth, half cycle has the number of teeth of tooth sector (34,34 ') of tooth and the number of teeth of crank gear (35,35 ') to equate, then when secondary crankshaft Rotate 180 °, axis and tooth sector half-twist.When tooth sector and crank gear engagement, secondary crankshaft and crank gear have unequal angular velocity.Crank 38 and 28 equal in length.Set up during installation when the piston work done finishes and reach lower dead center, when continuing the motion several angle, the tooth position that has of tooth sector 34 begins to mesh crank gear 35, at this moment crank 38 is in lower dead center, the certain angle of the leading crank of crank 28 38 then, claim that this angle is φ (for a following narration convenience), 0 °＜φ＜90 °.With shown in Figure 8, the air inlet control principle done one describe.Because above installation and selection, the top A point of valve stem 5 has identical amplitude and angular velocity with the top B point on valve top 41.Reach lower dead center when the piston work done finishes, piston 2 continues from lower dead center when top dead center moves the φ angle, and this moment, tooth sector 34 meshed with crank gear 35.This moment, the B point was in lower dead center.Cam 33 jack-up depression bars 37 are thrown off briquetting 36 and crank gear 35, crank gear 35 freedom, and crank 38 beginnings rotatablely move with crank gear 35 and drive valve top 41 and chase valve stem 5.Finish when piston 2 moves to piston 2 ' exhaust top dead center this moment, piston 2 returns to lower dead center from top dead center, and when motion φ/2, this moment, B point met with A point, and continuation is moved with regard to unseat the valve push rod 5, the realization air inlet.When continuing motion A point to lower dead center, this moment, valve stem 5 was still backed down, and when piston 2 reaches lower dead center and returns when carrying out φ/2 to top dead center, A point and B point will break away from, IC Intake Valve Closes, air inlet end.Realize the air inlet time-delay of φ/2 jiao.When the A point continued motion φ angle, the B point moved to lower dead center, and this moment, half cycle had tooth sector 35 engagements of tooth to finish, depression bar 37 is reduced to low spot by the height point along cam 33 under the effect of spring 42, briquetting 36 and crank gear 35 pressings, crank gear 35 location, promptly the B point is in lower dead center and does not move.Piston 2 continues motion and finishes compression and expansion space stroke, and valve stem 5 is closed gas-entered passageway all the time.The half cycle tooth sector that tooth sector 33 rotatablely moved anodontia in this process will mesh with crank gear again.Work done finishes and continues motion φ angle, repeats above course of action again.
Is identical for the control principle of exhaust and the selection of mechanism action mode and mechanism parameter with air inlet control.Just when mounted, during the certain angle φ of piston 2 ' work done range ability lower dead center, tooth sector 33 ' with crank gear 34 ' begin engagement, this moment valve top 41 ' summit B ' be in lower dead center, be crank 38 ' leading crank 28 φ angles, 0 °＜φ＜90 °.Valve stem 5 ' summit A ' and valve top 41 ' summit B ' motion principle as shown in Figure 9.When piston 2 ' work done moves to apart from lower dead center φ, this moment tooth sector 33 ' with crank gear 34 ' engagement, piston 2 ' continuation move distance lower dead center φ/2 o'clock, valve stem 5 ' A ' with valve top B ' meet, when continuing motion, valve stem 5 ' backed down, cylinder begins exhaust, has promptly realized the exhaust of φ/2 in advance jiao.When the last fulcrum φ of piston 2 ' run to distance/2, A ' will throw off with B ', valve stem 5 ' close exhaust passage, exhaust end.Cylinder is finished air inlet, when compression, on the position that B ' rests on lower dead center.
By the characteristics of above distribution device, can be and find out that when piston was in the middle of upper and lower stop, the distance that air valve backs down was maximum, and at this moment the speed of piston is also maximum.
In air inlet side and exhaust side the inlet and outlet closed box is arranged respectively.When exhaust stroke, the piston of air inlet side sucks air in the air inlet closed box because of pump-absorb action, also just stocks for follow-up intake stroke provides the pump suck.
At least four cylinders are arranged in parallel, and they can per two cylinders or the shared assembly mechanism of qi structure of multi cylinder more.
Work cycle differs the cylinder of 360 ° of crank angles, and its piston has identical motion.With four cylinders is example, the work cycle arrangement such as the following table of four cylinders:
| Cylinder | a | b | c | d |
| First stroke | Inhale | Alkene | Alkene | Inhale |
| Second stroke | Press | Row | Row | Press |
| Third trip | Alkene | Inhale | Inhale | Combustion |
| The fourth line journey | Row | Press | Press | Row |
Every a stroke two cylinder ad or bc work done are simultaneously arranged like this.The flywheel of installing on main crankshaft or main shaft only need help secondary crankshaft to cross non-power 180 °.The bc cylinder can a shared assembly mechanism of qi structure like this.
As shown in figure 10, be the unit with at least four cylinder conjugation-type diesel engines, can form the polynary secondary crankshaft of one deck and drive main crankshaft by vertical links, can be the unit also with at least four cylinder conjugation-type diesel engines, drive motion of main shaft by train of gearings.Form the polynary conjugation-type diesel engine of one deck.
Be the unit with at least four cylinders as shown in figure 11, the upper and lower two-layer secondary crankshaft of dual layer arrangement drives main crankshaft jointly.Each secondary crankshaft only need can guarantee that promptly main crankshaft and secondary crankshaft move in the same way by two vertical links as 43,44 like this.As shown in figure 12, vertical links 43 can be made an integral body, and vertical links 44 is identical with 43 structure.Vertical links 43,44 connects upper and lower secondary crankshaft and main crankshaft.If chat the form that four cylinders are example before adopting, and that the inlet and outlet side of upper and lower layer is installed is opposite, and each stroke does not all have cylinder to the main crankshaft work done and not intermittently like this.To form double-deck unit conjugation-type diesel engine.With at least four cylinders is the unit dual layer arrangement, and upper and lower two-layer secondary crankshaft also can form double-deck unit conjugation-type diesel engine by the train of gearings drive main spindle.
Certainly, be the unit with double-deck unit conjugation-type diesel engine, with the form of the polynary conjugation-type diesel engine of one deck, form polynary driving main crankshaft or main shaft, form double-deck polynary conjugation-type diesel engine.
For one deck or two-layer unit conjugation-type diesel engine, it is along with the increase of cylinder, and the connecting rod number that connects tranverse connecting rod and secondary crankshaft is constant, and the vertical links number of auxiliary connection bent axle and main crankshaft is constant.
The active force of the present invention's output all is symmetric form, makes more balance, more even of active force, has not only alleviated vibrations and noise, and has greatly reduced in the high compression ratio situation, the mechanical loss of bringing. And the inlet and outlet passage is loose, can strengthen air inflow, and is formed with the powerful eddy current of rule rate, thereby further improves empty combustion mixing rate. And reduced the lateral pressure of piston to cylinder sleeve, and be conducive to improve mechanical efficiency, prolong the service life of cylinder sleeve, improved the sealing of cylinder, simplified housing structure.
Claims (9)
1, a kind of multicylinder conjugate diesel engine with capless double-piston cylinders, it is characterized in that at least four cylinders are arranged in parallel, in each cylinder (1) lining two heterodromous each other pistons (2,2 ') are housed, the inlet and outlet door is positioned on respectively on the two-piston (2,2 '), surround the firing chamber by cylinder liner and two-piston, each piston of cylinder two ends homonymy (2,2 ') is by the fixedly connected tranverse connecting rod of piston rod (7,7 ') (10,10 '), the two-end part of tranverse connecting rod is positioned in the guide rail, and power take-off mechanism and the distribution device that transmits piston motion arranged.
2, diesel engine according to claim 1 is characterized in that piston 2 is made up of piston sleeve 3, piston cylinder 4 and piston rod 7, and the axis part of piston has gas-entered passageway, and is equipped with valve stem 5 and swirl vane 6 in passage; Piston 2 ' by piston sleeve 3 ', piston cylinder 4 ' and piston rod 7 ' form, the axis part of piston has the exhaust passage, and in passage, be equipped with valve stem 5 '.
3, diesel engine according to claim 2 is characterized in that the piston that gas-entered passageway is arranged of at least four cylinders is positioned on the same side of cylinder.
4, diesel engine according to claim 1 is characterized in that power take-off mechanism forms by be positioned on tranverse connecting rod (10,10 ') in the guide rail, connecting rod (12,12 ', 13,13 ') and the secondary crankshaft (14,14 ') of four cylinder both sides at the cylinder two ends at least.
5, diesel engine according to claim 4, it is characterized in that secondary crankshaft (14,14 ') can pass through vertical links (17,17 ', 18,18 ', 19,19 ') connect main crankshaft 15, secondary crankshaft also can mesh gear on the main shaft 16 by train of gearings, by 16 rotations of secondary crankshaft gear driven main shaft.By main crankshaft 15 or main shaft 16 outputting powers.
6, diesel engine according to claim 1 is characterized in that distribution device is made up of the depression bar (37,37 ') that is installed in timing gear (31,31 ') on the axis 32 and cam (33,33 ') and tooth sector (34,34 '), crank gear (35,35 '), two slidercrank mechanisms, is equipped with briquetting (36,36 ').
7, diesel engine according to claim 6, it is characterized in that tooth sector (33,33 ') engagement crank gear (34,34 '), be installed with the crank (37,37 ') of slidercrank mechanism on the crank gear, slide block (40,40 ') at slidercrank mechanism is equipped with valve top (41,41 '), timing gear (31,31 ') on timing gear (30,30 ') the engagement pair bent axle, an end of depression bar (37,37 ') withstands on the cam.
8, diesel engine according to claim 7, the number of teeth that it is characterized in that the timing gear (31,31 ') on the axis 32 is two times of secondary crankshaft (14,14 ') timing gear (30, the 30 ') number of teeth, and half cycle has the number of teeth of tooth sector (34,34 ') of tooth and the number of teeth of crank gear (35,35 ') to equate.
9, diesel engine according to claim 1 is characterized in that with at least four cylinder conjugation-type diesel engines being that the unit constitutes the polynary conjugation-type diesel engine of one deck or two layers or two layers of polynary conjugation-type diesel engine.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN86108669.4A CN1004218B (en) | 1986-12-17 | 1986-12-17 | Multicylinder conjugate diesel engine with capless double-piston cylinders |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN86108669.4A CN1004218B (en) | 1986-12-17 | 1986-12-17 | Multicylinder conjugate diesel engine with capless double-piston cylinders |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN86108669A true CN86108669A (en) | 1988-06-29 |
| CN1004218B CN1004218B (en) | 1989-05-17 |
Family
ID=4804007
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN86108669.4A Expired CN1004218B (en) | 1986-12-17 | 1986-12-17 | Multicylinder conjugate diesel engine with capless double-piston cylinders |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1004218B (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101975111A (en) * | 2010-10-15 | 2011-02-16 | 靳北彪 | Piston crank mechanism of combined cylinder |
| CN102817659A (en) * | 2011-08-29 | 2012-12-12 | 摩尔动力(北京)技术股份有限公司 | Crank cam valve actuating mechanism |
| CN103470373A (en) * | 2013-09-06 | 2013-12-25 | 陈鑫 | Single-cylinder multiple-piston engine with pistons arranged in opposite manner and crankshafts arranged in opposite manner |
| CN112112698A (en) * | 2020-09-22 | 2020-12-22 | 东风汽车集团有限公司 | Camshaft drive structure and fuel engine |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102606242A (en) * | 2011-08-23 | 2012-07-25 | 靳北彪 | Valve actuating mechanism for reciprocating motion body |
-
1986
- 1986-12-17 CN CN86108669.4A patent/CN1004218B/en not_active Expired
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101975111A (en) * | 2010-10-15 | 2011-02-16 | 靳北彪 | Piston crank mechanism of combined cylinder |
| WO2012048508A1 (en) * | 2010-10-15 | 2012-04-19 | Jin Beibiao | Combined cylinder piston crank mechanism |
| CN102817659A (en) * | 2011-08-29 | 2012-12-12 | 摩尔动力(北京)技术股份有限公司 | Crank cam valve actuating mechanism |
| CN102817659B (en) * | 2011-08-29 | 2015-09-02 | 摩尔动力(北京)技术股份有限公司 | Crankshaft cam distribution device |
| CN103470373A (en) * | 2013-09-06 | 2013-12-25 | 陈鑫 | Single-cylinder multiple-piston engine with pistons arranged in opposite manner and crankshafts arranged in opposite manner |
| CN112112698A (en) * | 2020-09-22 | 2020-12-22 | 东风汽车集团有限公司 | Camshaft drive structure and fuel engine |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1004218B (en) | 1989-05-17 |
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