CN105569843A - Engine transmission device for replacing crankshaft-connecting rod mechanism - Google Patents
Engine transmission device for replacing crankshaft-connecting rod mechanism Download PDFInfo
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- CN105569843A CN105569843A CN201510978706.XA CN201510978706A CN105569843A CN 105569843 A CN105569843 A CN 105569843A CN 201510978706 A CN201510978706 A CN 201510978706A CN 105569843 A CN105569843 A CN 105569843A
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- tooth
- groove
- tooth bar
- sector
- pins
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/40—Other reciprocating-piston engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
- F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
- F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
- F16H19/043—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack for converting reciprocating movement in a continuous rotary movement or vice versa, e.g. by opposite racks engaging intermittently for a part of the stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H19/00—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion
- F16H19/02—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion
- F16H19/04—Gearings comprising essentially only toothed gears or friction members and not capable of conveying indefinitely-continuing rotary motion for interconverting rotary or oscillating motion and reciprocating motion comprising a rack
- F16H2019/046—Facilitating the engagement or stopping of racks
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transmission Devices (AREA)
Abstract
Provided is an engine transmission device for replacing a crankshaft-connecting rod mechanism. According to the engine transmission device, a sector gear 2 on a spindle 1 is arranged on a rectangular rack frame formed by a rack 3, a rack 4, a rack connecting plate 5 and a rack connecting plate 6, the sector gear 2 is alternately engaged with the rack 3 and the rack 4, short guide grooves 701, driving grooves 702 and reversing grooves 703 in the inner sides of two rotary arms 7 can be alternately in linkage with driving pins 501 on the two side faces of the rack connecting plate 5 and driving pins 601 on the two side faces of the rack connecting plate 6, a guide groove 305 in the bottom face of the rack 3 and a guide groove 405 in the bottom face of the rack 4 are formed in guide rails 8 on the inner wall of a shell 9, and one end of the rack 3 and one end of the rack 4 are connected through connecting rods 10 and pistons 11 in two air cylinders 12 to form a dual-cylinder engine set. According to the transmission device, the mechanical conversion efficiency is greatly improved, and lateral friction force between the pistons 11 and cylinder walls is thoroughly eliminated.
Description
Technical field
The present invention relates to the driving mechanism that a kind of linear reciprocating motion is converted to circular movement, in particular to a kind of engine-driven gearing replacing crankshaft & connecting, with the mutual conversion efficiency of linear reciprocating motion and rotary motion improving motor, eliminate the lateral pressure between piston and cylinder wall.
Background technique
In mechanical engineering, such as reciprocating engine, compressor and some other machinery needing to carry out straight reciprocating motion and circular movement and mutually change, bent axle (crank) the connecting rod switching mechanism generally adopted at present, but, no matter from theory analysis, or bent axle traditional in practical application (handle) linkage mechanism is established and all be there is intrinsic defect:
1, in bent axle (handle) linkage mechanism, the gaseous-pressure acted on piston be broken down into along connecting rod axial direction active force and act on the side pressure of casing wall perpendicular to cylinder axis direction, increase the side-friction force between piston and casing wall, accelerate cylinder wall side wear, not only reduce the mechanical efficiency of piston, but also can cause " card cylinder " that piston cannot be worked;
2, the active force along connecting rod axial direction acted on bent axle (handle) is decomposed into the tangential force of vertical crankshaft radial direction and the normal force along radial direction again, in combustion gas outburst moment, because transmission angle is very little, the tangential forces of the moment of torsion exported is much smaller than the gaseous-pressure on piston, when having calculating to show that transmission angle is 10 degree, piston total force only has 20 percent left/right rotation to be changed to the tangential forces producing crank torque;
3, the uneven rotating mass that in crankshaft & connecting, connecting rod swing produces and rotation motion cause inertial force, make piston and cylinder wall and rotate surface of contact to produce change impacts power, increase the uneven friction between all parts and shock, not only affect the output power of motor, and make motor produce larger vibration & noise.
Summary of the invention
The technical problem to be solved in the present invention is to provide a kind of tooth sector and cursor and combines and drive the switching mechanism of tooth bar to substitute traditional bent axle (handle) linkage mechanism, to overcome the intrinsic above-mentioned defect of bent axle-jointed gear unit, be a kind of straight reciprocating motion unlike the prior art and circular movement conversion equipment.
A kind of engine-driven gearing structure replacing bent axle-linkage mechanism of the present invention is as described below:
The tooth sector that main shaft in housing is arranged is placed in the tooth bar framework be made up of the first tooth bar and the second tooth bar and the first tooth bar connecting plate and the second tooth bar connecting plate, one end of two cursors that the main shaft cylinder of tooth sector both sides is identical with shape is rigidly connected, two cursors are symmetrical about longitudinal middle section of tooth sector, if when setting main shaft and tooth sector and two cursors rotate counterclockwise, the inner side surface of two cursor symmetries is offered the short groove of guiding and the driver slot of connection respectively along clockwise direction successively and turns to groove, if when setting main shaft and tooth sector and two cursors rotate clockwise, the inner side surface of two cursor symmetries is offered the short groove of guiding and the driver slot of connection respectively in the counterclockwise direction successively and turns to groove, two guide short groove, two driver slots, two turn to the shape of groove identical, and it is symmetrical about longitudinal middle section of tooth sector, two guide short groove, two driver slots and two thickness turning to the groove depth of groove to be less than two cursors, the bi-side of the first tooth bar connecting plate and the second tooth bar connecting plate arrange the first drive pin of coaxial line and the second drive pin of coaxial line respectively, the axis of the first drive pin and the second drive pin is positioned on the horizontal middle section of the first tooth bar connecting plate and the second tooth bar connecting plate, short groove and two driver slots and two are guided to turn to wall energy in two ledges of groove alternately to slide on the cylinder of two the first drive pins and two the second drive pins, two cursors and the first tooth bar and the second tooth bar are linked, the first guiding groove offered at the back side of the first tooth bar and the second tooth bar and the second guiding groove are placed on two guard rails respectively, the one end portion of the first tooth bar and the second tooth bar does not does not connect and compose single cylinder or multicylinder engine group with the piston in each cylinder respectively by connecting rod.
In engine-driven gearing of the present invention, tooth sector is connected with main shaft cylinder coaxial rigid, the thickness of tooth sector is equal with the thickness of two tooth bars, central angle corresponding to the tooth top cambered surface of the tooth sector gear teeth is more than or equal to 90 ° and is less than 180 °, the gear teeth quantity of tooth sector is less than the number of teeth of two tooth bars, and tooth sector can replace and engages with the first tooth bar and the second tooth bar.
In engine-driven gearing of the present invention, the width of the first guiding groove and the second guiding groove equals two guard rail thickness, the top of two guard rails is placed in the first guiding groove and the second guiding groove respectively, and the bottom of two guard rails is arranged on the inwall of housing respectively.
In engine-driven gearing of the present invention, two the first knuckle pins are the cylinder that shape is identical with two the second knuckle pins, two the first knuckle pins are parallel with the axis of two the second knuckle pins and the main axis of main shaft, the diameter of two the first knuckle pins and two the second knuckle pins equals two width guiding short grooves and two driver slots and two to turn to groove, and the height of two the first drive pins and two the second drive pins equals two groove depths guiding short grooves and two driver slots and two to turn to groove.
In engine-driven gearing of the present invention, two guide the shape of short groove as described below: if when tooth sector is for rotating clockwise, before the second end gear teeth of tooth sector and the first time end tooth of the first tooth bar that engages with it depart from, the inner side surface of two the first knuckle pins of translation and two cursors of rotation does compound motion, the track that two the first knuckle pins move at two cursor inner side surfaces guides the shape of short groove identical with two, two guide short grooves and enter notch and can replace and slide on the cylinder of two the first knuckle pins, before the second end gear teeth of tooth sector and the second time end tooth of the second tooth bar depart from, the inner side surface of two the second knuckle pins of translation and two cursors of rotation does compound motion, the track that two the second knuckle pins move at two cursor inner side surfaces guides the shape of short groove identical with two, two guide short grooves and enter notch and can replace relative sliding on two the second knuckle pin cylinders, if when tooth sector is for rotating counterclockwise, before the first end gear teeth of tooth sector and the first time end tooth of the second tooth bar depart from, the inner side surface of two the first knuckle pins of translation and two cursors of rotation does compound motion, the track that two the first knuckle pins move at two cursor inner side surfaces guides the shape of short groove identical with two, two guide short grooves and enter notch and can replace at two the first knuckle pin cylinder relative slidings, before the first end gear teeth of tooth sector and the second time end tooth of the first tooth bar depart from, the inner side surface of two the second knuckle pins of translation and two cursors of rotation does compound motion, the track that two the second knuckle pins move at two cursor inner side surfaces guides the shape of short groove identical with two, two guide short grooves and enter notch and can replace at two the second knuckle pin cylinder relative slidings.
In engine-driven gearing of the present invention, two driver slots can be curvilinear groove or skewed slot, two smooth joining places of notch that enter going out notch and two driver slots guiding short grooves are first be connected port, the notch that goes out of two driver slots turns to the smooth rank place that connects of notch of entering of groove second to be connected port with two, two first be connected port to main shaft main axis between distance be greater than the spacing of the second linking port to the main axis of main shaft; If tooth sector is for rotating counterclockwise, the second end gear teeth of tooth sector and the second tooth bar first time, end tooth departed from time
,two the first drive pins are connected port first, and when the second end gear teeth of tooth sector and the second time end tooth of the first tooth bar depart from, two the second drive pins are connected port second; If tooth sector is for rotating clockwise, the first end gear teeth of tooth sector and the first time of the first tooth bar, end tooth departed from time, two the first drive pins are connected port at two first, when the first end gear teeth of tooth sector and the second time end tooth of the second tooth bar depart from, drive pin is connected port at two second.
In engine-driven gearing of the present invention, two turn to groove to be curvilinear groove, second of the notch that enters of groove is turned to be connected port at the notch that goes out of two driver slots with two, the end of driver slot and two turn to the end of groove circumscribed, two radiuses turning to the radius of curvature of groove to be greater than two drive pins and two drive pins, two turn to the distance entered between notch to main axis of groove to be less than distances gone out between notch main axis that two turn to groove, if tooth sector is for rotating counterclockwise: two one or two drive pins are when two driver slots turn to two of groove second to be connected port with two, the first end gear teeth of tooth sector are at the first end tooth of the first tooth bar with for the first time between end tooth, two turn to groove go out notch and two the first drive pins when departing from, the first end gear teeth of tooth sector engage with the first end tooth of the first tooth bar and second time end tooth, two the second drive pins are when being connected port for two second, the first end gear teeth of tooth sector are between second end tooth and second time end tooth of the second tooth bar, two turn to groove go out notch and two the second drive pins when departing from, the first end gear teeth of tooth sector engage with the second end tooth of the second tooth bar and second time end tooth, if set tooth sector as rotating clockwise: two one or two drive pins are when second is connected port, the first end gear teeth of tooth sector are at the first end tooth of the second tooth bar with for the first time between end tooth, two turn to groove go out notch and two the first drive pins when departing from, the first end gear teeth of tooth sector engage with the first end tooth of the second tooth bar and time first end tooth, two the second drive pins are when being connected port for two second, the first end gear teeth of tooth sector are between second end tooth and second time end tooth of the first tooth bar, two turn to groove go out notch and two the second drive pins when departing from, the first end gear teeth of tooth sector engage with the second end tooth of the first tooth bar and second time end tooth.
In engine-driven gearing of the present invention, the prolongation at tooth bar and tooth bar two ends is rigidly connected with the first tooth bar connecting plate and the second tooth bar connecting plate two end part respectively, equal or the thickness that is less than with the first tooth bar and the second tooth bar of the thickness of the first tooth bar connecting plate and the second tooth bar connecting plate, the axis of main shaft is equal to the distance of the Topland of the first tooth bar and the second tooth bar, and the distance between the reticule of the first tooth bar and the second tooth bar equals the standard pitch diameter of tooth sector.
In engine-driven gearing of the present invention, the two end part of the first tooth bar and the second tooth bar connect and compose opposed four cylinder engine group with the piston in four cylinders respectively by connecting rod respectively.
The main shaft of transmission device of the present invention turns with the rotating shaft of motor and is connected, and the rotary motion of motor is converted to the mechanical device of linear reciprocating motion.
The engine-driven gearing of replacement bent axle-linkage mechanism of the present invention has the following advantages:
1. transmission device provided by the invention adopts the kind of drive of fan tooth wheel and rack engagement, the total force in piston axis direction is made to act directly on the tangent direction of tooth sector by tooth bar, piston axis direction total force equals the tangential force of tooth sector output torque, improve engine output torque, completely eliminate in bent axle-connecting rod switching mechanism and produce lateral pressure between piston and cylinder wall, the cylinder wall side wear avoided and caused by side-friction force and " card cylinder ", improve the efficiency of motor, extend the working life of cylinder.
2. in transmission device provided by the invention, after fan tooth wheel and rack departs from engagement, linked by the drive pin of the driver slot on cursor and tooth bar connecting plate, slow down gradually before making its stop of piston arrives, the momentum of tooth bar and connecting rod and piston, in the stop place smooth conversion of piston stroke, decreases momentum loss as bent axle-linkage mechanism.
3., in transmission device provided by the invention, drive tooth bar reversing motion by the drive pin of groove and tooth bar connecting plate that turns on cursor, the end gear teeth of tooth sector can absence of collision be engaged with the end tooth of tooth bar.
The transmission device of replacement crankshaft & connecting of the present invention also can be used for the machinery that any type of rotary motion is converted to linear reciprocating motion, such as, and piston type oil, gas and water pump and compressor etc.
Accompanying drawing explanation
Fig. 1 is a kind of plan view replacing engine-driven gearing first embodiment of bent axle-linkage mechanism of the present invention.
Fig. 2 is B-B direction vertical view cutaway drawing in the first embodiment of the present invention.
Fig. 3 is that in the first embodiment of the present invention, C-C analyses and observe in direction.
Fig. 4 is in first embodiment of the invention, guides short groove, driver slot, turns to groove and drive pin schematic diagram.
Fig. 5 is in first embodiment of the invention, and the second drive pin enters notch schematic diagram the short groove of guiding.
Fig. 6 is in first embodiment of the invention, and the first drive pin is connected port schematic diagram what guide short groove and driver slot.
Fig. 7 is in first embodiment of the invention, the first drive pin driver slot with turn to groove be connected port schematic diagram.
Fig. 8 is in first embodiment of the invention, and the first drive pin goes out notch schematic diagram what turn to groove.
Fig. 9 is in first embodiment of the invention, and the second drive pin is connected port schematic diagram what guide short groove and driver slot.
Figure 10 is in first embodiment of the invention, the second drive pin driver slot with turn to groove be connected port schematic diagram.
Figure 11 is in first embodiment of the invention, and the second drive pin goes out notch schematic diagram what turn to groove.
Figure 12 is that engine-driven gearing of the present invention forms four cylinder engine group schematic diagram.
The main shaft of Figure 13 transmission device of the present invention turns with the rotating shaft of motor and is connected, and the rotary motion of motor is converted to the mechanical device schematic diagram of linear reciprocating motion.
Embodiment
Describe the specific embodiment of the present invention in detail with reference to the accompanying drawings:
A kind of engine-driven gearing first embodiment replacing bent axle-linkage mechanism of the present invention, as Fig. 1, 2, shown in 3, main shaft 1 is arranged on two walls of housing 9, main shaft 1 in housing 9 fixedly mounts coaxial tooth sector 2, even the tooth bar framework formed that is rigidly connected is held to be enclosed within tooth sector 2 by tooth bar 3 and tooth bar 4 two ends prolongation with tooth bar connecting plate 5 and tooth bar connecting plate 6, one end of two cursors 7 that main shaft 1 cylinder of tooth sector 2 both sides is identical with shape is rigidly connected, two cursors 7 are symmetrical about longitudinal middle section of tooth sector 2, set main shaft 1 and tooth sector 2 and two cursors 7 to rotate clockwise, the inner side surface of two cursor 7 symmetries is offered the short groove 701 of guiding and the driver slot 702 of connection successively and turns to groove 703, the bi-side of tooth bar connecting plate 5 and the horizontal middle section of tooth bar connecting plate 6 arrange the drive pin 501 of coaxial line and the drive pin of coaxial line respectively, two guide short groove 701, two driver slots 702 and two turn to groove 703 to replace and slide on the cylinder of drive pin 501 and two drive pins 601, two cursors 7 are linked with tooth bar 3 and tooth bar 4, the guiding groove 305 offered at the back side of tooth bar 3 and tooth bar 4 and guiding groove 405 are placed on guard rail 8 respectively, the one end portion of tooth bar 3 and tooth bar 4 does not does not connect and compose single cylinder or multicylinder engine group with the piston 11 in each cylinder 12 respectively by connecting rod 10.
In the first embodiment of the present invention, as shown in Figure 1, 2, tooth sector 2 is connected with main shaft 1 cylinder coaxial rigid, the thickness of tooth sector 2 is equal with the thickness of tooth bar 3 and tooth bar 4, the central angle of tooth top cambered surface 201 correspondence of tooth sector 2 gear teeth equals 120 °, the gear teeth quantity of tooth sector 2 is less than the number of teeth of tooth bar 3 and tooth bar 4, and tooth sector 2 can replace and engages with tooth bar 3 and tooth bar 4.
In the first embodiment of the present invention, as shown in Figure 1,3, the width of guiding groove 305 and guiding groove 405 equals guard rail 8 thickness, and the bottom that the top of two guard rails 8 is placed in guiding groove 305 and guiding groove 405, two guard rails 8 is respectively arranged on housing 9 inwall respectively.
In the first embodiment of the present invention, as shown in Fig. 1,2,4, two knuckle pins 501 are the cylinder that shape is identical with two knuckle pins 601, one end of two knuckle pins 501 and two knuckle pins 601 and the bi-side of tooth bar connecting plate 5 and tooth bar connecting plate 6 are rigidly connected, the axis of the axis of two knuckle pins 501 and two knuckle pins 601 is on tooth bar connecting plate 5 and the horizontal middle section of tooth bar connecting plate 6, and parallel with the main axis 101 of main shaft 1.
In the first embodiment of the present invention, as Fig. 2, shown in 4, two guide short groove 701, two driver slots 702, two turn to the shape of groove 703 identical, and the longitudinal middle section separately about tooth sector 2 is symmetrical, two guide short groove 701, two driver slots 702 and two thickness turning to the groove depth of groove 703 to be less than two cursors 7, the diameter of two knuckle pins 501 and two knuckle pins 601 equals two width guiding short grooves 701 and two driver slots 702 and two to turn to groove 703, the height of two drive pins 501 and two drive pins 601 equals two groove depths guiding short grooves 701 and two driver slots 702 and two to turn to groove 703, two guide short grooves 701 go out notch and two driver slots 702 enter the smooth joining place of notch for being connected port 705, two driver slots 702 go out notch with two turn to groove 703 enter the smooth joining place of notch for being connected port 706.
In the first embodiment of the present invention, as Fig. 1, shown in 5, two guide the shape of short grooves 701 as described below: before the second end gear teeth 203 of tooth sector 2 and the secondary end tooth 302 of tooth bar 3 that engages with it depart from, two knuckle pins 501 of translation do compound motion with the inner side surface of two cursors 7 rotated, the track that two knuckle pins 501 move at two cursor 7 inner side surfaces guides the shape of short groove 701 identical with two, two guide short grooves 701 and enter notch 704 and can replace at two knuckle pin 501 cylinder relative slidings, before the second end gear teeth 203 of tooth sector 2 and the second time end tooth 403 of tooth bar 4 depart from, two knuckle pins 601 of translation do compound motion with the inner side surface of two cursors 7 rotated, the track that two knuckle pins 601 move at two cursor 7 inner side surfaces guides the shape of short groove 701 identical with two, two guide short grooves 701 and enter notch 704 and can replace at two knuckle pin 601 cylinder relative slidings.
In the first embodiment of the present invention, as shown in Figure 2,4, two driver slots 702 can be curvilinear groove, be connected port 705 to main shaft 1 main axis 101 between distance be greater than two and be connected the spacing that ports 706 arrive the main axis 101 of main shaft 1; As shown in Figure 6, when the first time end tooth 302 of the first end gear teeth 201 of tooth sector 2 and tooth bar 3 departs from, drive pin 501 is connected ports 705 at two, as shown in Figure 7, when the first end gear teeth 201 of tooth sector 2 depart from the second time end tooth 403 of tooth bar 4, drive pin 601 is at linking port 705.
In the first embodiment of the present invention, as shown in Figure 2,4, two turn to groove 703 for curvilinear groove, driver slot 702 go out notch with two turn to groove 703 be connected port 706, the end of driver slot 702 and two turn to the end of groove 703 circumscribed, two radiuses turning to the radius of curvature of groove 703 to be greater than two drive pins 501 and two drive pins 601, two turn to the distance entered between notch 706 to main axis 101 of groove 703 to be less than distances gone out between notch 707 to main axis that two turn to groove 703, as shown in Figure 8, two drive pins 501 driver slot 702 go out notch with two turn to groove 703 be connected port 706 time, the first end gear teeth 201 of tooth sector 2 are at the first end tooth 401 of tooth bar 4 with for the first time between end tooth 402, as shown in Figure 9, two drive pins 601 driver slot 702 go out notch with two turn to groove 703 be connected port 706 time, the first end gear teeth 201 of tooth sector 2 are between second end tooth 304 and second time end tooth 303 of tooth bar 3, as shown in Figure 10, two turn to groove 703 go out notch 707 and two drive pins 501 when departing from, the first end gear teeth 201 of tooth sector 2 engage with the end tooth 401 of tooth bar 4 and time end tooth 402, as shown in figure 11, two turn to groove 703 go out notch 707 and two drive pins 601 when departing from, the first end gear teeth 201 of tooth sector 2 engage with the end tooth 304 of tooth bar 3 and time end tooth 303.
In the first embodiment of the present invention, as shown in Figure 1, 2, 3, the prolongation at tooth bar 3 and tooth bar 4 two ends is rigidly connected with tooth bar connecting plate 5 and tooth bar connecting plate 6 two end part respectively, equal or the thickness that is less than with tooth bar 3 and tooth bar 4 of the thickness of tooth bar connecting plate 5 and tooth bar connecting plate 6, the axis of main shaft 1 is equal to the distance of the Topland of tooth bar 3 and tooth bar 4, and the distance between the reticule of tooth bar 3 and tooth bar 4 equals the standard pitch diameter of tooth sector 2.
The second embodiment of the present invention, with reference to shown in Figure 12, in transmission device of the present invention, tooth bar 3 is connected with the piston 11 in each cylinder 12 by two connecting rods 10 respectively with an end of tooth bar 4, tooth bar 3 is connected with the piston 11 in each cylinder 12 by two connecting rods 10 respectively with the other end of tooth bar 4, forms opposed four cylinder engine group.
As shown at 13, the main shaft 1 of transmission device of the present invention is connected with the rotating shaft of motor, the rotary motion of motor 14 is converted to the mechanical device of linear reciprocating motion.
A kind of running replacing engine-driven gearing first embodiment of bent axle-linkage mechanism provided by the invention is as described below: with reference to shown in Fig. 1, the shape gear 2 rotated clockwise drives tooth bar 3 and piston 11 to move to top dead center, before the second end gear teeth 203 of tooth sector 2 and the secondary end tooth 302 of tooth bar 3 engaged with it depart from, two guide the notch 704 that enters of short groove 701 to turn on two knuckle pin 501 cylinders, subsequently, two guide short groove 701 to slide on two knuckle pin 501 cylinders.
As shown in Figure 6, when the second end gear teeth 203 of tooth sector 2 depart from the secondary end tooth 302 of tooth bar 3, drive pin 501 is at linking port 705 place of driver slot 702, subsequently, two ledges of two driver slots 702 slide on the cylinder of drive pin 501, because the linking port 705 of two driver slots 702 to be greater than the distance of linking port 706 to main axis 101 of two driver slots 702 to the distance of main axis 101, two driver slots 702 that two drive pin 501 cylinders slide drive tooth bar 3 and piston 13 to continue to move to top dead center.
As shown in Figure 8, when two driver slots 702 and two turn to the linking port 706 of groove 703 to slide into two drive pins 501, the end gear teeth 202 of tooth sector 2 are between the tooth 401 and secondary end tooth 402 of tooth bar 4, when turning to groove 703 to slide on two drive pins 501 for two, due to two turn to the linking port 706 of groove 703 to the distance of main axis 101 be less than two turn to groove 703 go out the distance of notch 707 to main axis 101, two turn to groove 703 to drive tooth bar 4 to start to move to lower dead center by two drive pins 501, end tooth 401 and time end tooth 402 is synchronous with the end gear teeth 202 of tooth sector 2 moves in the same way.
As shown in Figure 10, when two turn to groove 703 go out notch 707 and two drive pins 501 depart from time, the first end gear teeth 202 of tooth sector 2 engage with the end tooth 401 of tooth bar 4 and time end tooth 402 absence of collision, and the tooth bar 4 engaged with tooth sector 2 drives piston 11 to continue to move to lower dead center.
As shown in Figure 5, before the second end gear teeth 203 of tooth sector 2 and the secondary end tooth 403 of tooth bar 4 depart from, two guide the notch 704 that enters of short groove 701 to turn on two knuckle pin 601 cylinders, and subsequently, two guide short groove 701 to slide on two knuckle pin 601 cylinders.
As shown in Figure 7, when the second end gear teeth 203 of tooth sector 2 depart from the secondary end tooth 403 of tooth bar 4, drive pin 601 is at linking port 705 place of driver slot 702, subsequently, two ledges of two driver slots 702 slide on the cylinder of drive pin 601, because the linking port 705 of two driver slots 702 to be greater than the distance of linking port 706 to main axis 101 of two driver slots 702 to the distance of main axis 101, two driver slots 702 that two drive pin 601 cylinders slide drive tooth bar 4 and piston 11 to continue to move to lower dead center.
As shown in Figure 9, when two driver slots 702 and two turn to the linking port 706 of groove 703 to slide into two drive pins 601, the end gear teeth 202 of tooth sector 2 are between the secondary end tooth 303 and end tooth 304 of tooth bar 3, when turning to groove 703 to slide on two drive pins 601 for two, due to two turn to the linking port 706 of groove 703 to the distance of main axis 101 be less than two turn to groove 703 go out the distance of notch 707 to main axis 101, two turn to groove 703 to drive tooth bar 3 to start to move to top dead center by two drive pins 601, secondary end tooth 303 and end tooth 304 is synchronous with the end gear teeth 202 of tooth sector 2 moves in the same way.
As shown in figure 11, when two turn to groove 703 go out notch 707 and two drive pins 601 depart from time, the first end gear teeth 202 of tooth sector 2 engage with the secondary end tooth 303 of tooth bar 3 and end tooth 304 absence of collision, the tooth bar 3 engaged with tooth sector 2 drives piston 11 to continue to move to top dead center, and the shape gear 2 rotated clockwise drives tooth bar 3 and piston 11 to move to top dead center.
Transmission device of the present invention is in above-mentioned running, and tooth bar 3 and tooth bar 4 reciprocatingly slide respectively by the guiding groove 305 at its back side and guiding groove 405 on guard rail 8.
Before the second end gear teeth 203 of tooth sector 2 depart from the secondary end tooth 302 of tooth bar 3 again, two guide the notch 704 that enters of short groove 701 again to turn on two knuckle pin 501 cylinders, other relevant all parts of transmission device of the present invention will repeat above-mentioned running again and again, the linear reciprocating motion of each piston 13 are converted to tooth sector 2 and the unidirectional circular movement of main shaft 1.
Above embodiment is described the preferred embodiment of the present invention; not scope of the present invention is limited; under not departing from the present invention and designing the prerequisite of spirit; related domain engineers and technicians make various distortion and improvement to technological scheme of the present invention, all should fall in protection domain that claims of the present invention determine.
Claims (10)
1. one kind replaces the engine-driven gearing of bent axle-linkage mechanism, it is characterized in that: the main shaft (1) being arranged on housing (9) two side arranges tooth sector (2), described tooth sector (2) is placed in the tooth bar framework be made up of with the first tooth bar connecting plate (5) and the second tooth bar connecting plate (6) the first tooth bar (3) and the second tooth bar (4), one end of two cursors (7) that the main shaft (1) of described tooth sector (2) both sides is identical with shape is rigidly connected, described two cursors (7) are symmetrical about longitudinal middle section of tooth sector (2), if when setting main shaft (1) and tooth sector (2) and two cursors (7) rotate clockwise, respectively according to counterclockwise offering the short groove of guiding (701) and the driver slot (702) of connection and turn to groove (703) on the inner side surface that two cursors (7) are symmetrical, if when setting main shaft (1) and tooth sector (2) and two cursors (7) rotate counterclockwise, the inner side surface that two cursors (7) are symmetrical is offered the short groove of guiding (701) and the driver slot (702) of connection according to clockwise direction respectively and turned to groove (703), the bi-side of described tooth bar connecting plate (5) and tooth bar connecting plate (6) install first drive pin (501) of coaxial line and second drive pin (601) of coaxial line respectively, the first guiding groove (305) that the back side of described tooth bar (3) and tooth bar (4) is offered and the second guiding groove (405) are placed on guard rail (8) respectively, one end of described tooth bar (3) and tooth bar (4) or two end part connect and compose single cylinder or multicylinder engine group by connecting rod (10) and the piston (11) in each cylinder (12) respectively.
2. engine-driven gearing according to claim 1, it is characterized in that: described tooth sector (2) is connected with main shaft (1) cylinder coaxial rigid, the thickness of tooth sector (2) is equal with the thickness of tooth bar (3) and tooth bar (4), the central angle of tooth top cambered surface (201) correspondence of tooth sector (2) gear teeth is more than or equal to 90 ° and is less than 180 °, the gear teeth quantity of tooth sector (2) is less than the number of teeth of tooth bar (3) and tooth bar (4), and tooth sector (2) can replace and engages with tooth bar (3) and tooth bar (4).
3. engine-driven gearing according to claim 1, it is characterized in that: the width of described guiding groove (305) and guiding groove (405) equals guard rail (8) thickness, the top of two guard rails (8) is placed in guiding groove (305) and guiding groove (405) respectively, and the bottom of two guard rails (8) is arranged on the relative inwall of housing (9) respectively.
4. engine-driven gearing according to claim 1, it is characterized in that: described two knuckle pins (501) and two knuckle pins (601) are the identical cylinder of shape, the axis of two knuckle pins (501) and the axis of two knuckle pins (601) are on tooth bar connecting plate (5) and tooth bar connecting plate (6) horizontal middle section, and the axis of two knuckle pins (501) is parallel with the main axis (101) of main shaft (1) with the axis of two knuckle pins (601).
5. according to claim 1, engine-driven gearing described in 4, it is characterized in that: described two guide short groove (701), two driver slots (702), two turn to the shape of groove (703) identical, and the longitudinal middle section separately about tooth sector (2) is symmetrical, two guide short groove (701) and two driver slots (702) and two thickness turning to the groove depth of groove (703) to be less than two cursors (7), two guide short groove (701) and two driver slots (702) and two diameters turning to the width of groove (703) to equal two knuckle pins (501) and two knuckle pins (601), two guide short groove (701) and two driver slots (702) and two to turn to the groove depth of groove (703) to equal or slightly larger than the height of two drive pins (501) and two drive pins (601), the groove inner wall smooth joining place that two groove inwalls guiding short groove (701) to go out notch and two driver slots (702) enter notch is first be connected port (705), the groove inwall that two driver slots (702) go out notch and two groove inner wall smooth joining places turning to groove (703) to enter notch are second be connected port (706).
6. according to claim 1, engine-driven gearing described in 5, it is characterized in that: described two guide the shape of short groove (701) as described below: if when described tooth sector (2) is for rotating clockwise, before the second end gear teeth (203) of tooth sector (2) and the first time end tooth (302) of tooth bar (3) that engages with it depart from, two knuckle pins (501) of translation are compound motion with the inner side surface of two cursors (7) rotated, the track that two knuckle pins (501) are moved at two cursor (7) inner side surfaces guides the shape of short groove (701) identical with described two, two guide short groove (701) and enter notch (704) and can replace relative sliding on two knuckle pin (501) cylinders, before the second end gear teeth (203) of tooth sector (2) depart from the second time end tooth (403) of tooth bar (4), two knuckle pins (601) of translation and the inner side surface compound motion each other of two cursors (7) rotated, the track that two knuckle pins (601) are moved at two cursor (7) inner side surfaces guides the shape of short groove (701) identical with described two, two guide short groove (701) and enter notch (704) and can replace at two knuckle pin (601) cylinder relative slidings, if when tooth sector (2) is for rotating counterclockwise, before the first end gear teeth (202) of described tooth sector (2) depart from the first time end tooth (402) of tooth bar (4), two knuckle pins (501) of translation and the inner side surface compound motion each other of two cursors (7) rotated, the track that two knuckle pins (501) are moved at two cursor (7) inner side surfaces guides the shape of short groove (701) identical with two, two guide short groove (701) and enter notch (704) and can replace at two knuckle pin (501) cylinder relative slidings, before the first end gear teeth (202) of described tooth sector (2) depart from the second time end tooth (303) of tooth bar (3), two knuckle pins (601) of translation and the inner side surface compound motion each other of two cursors (7) rotated, the track that two knuckle pins (601) are moved at two cursor (7) inner side surfaces guides the shape of short groove (701) identical with two, two guide short groove (701) and enter notch (704) and can replace at two knuckle pin (601) cylinder relative slidings.
7. according to claim 1, engine-driven gearing described in 6, it is characterized in that: described two driver slots (702) can be curvilinear groove or skewed slot, described linking port (705) to main shaft (1) main axis (101) between distance be greater than described two and be connected port (706) to the spacing of the main axis (101) of main shaft (1), the mounting type of two drive pins (501) and two drive pins (601) and two driver slots (702) is as described below: if tooth sector (2) is for rotating clockwise, when the second end gear teeth (203) of tooth sector (2) depart from the first time end tooth (302) of tooth bar (3), described two drive pins (501) are connected port (705) at described two, when the first end gear teeth (202) of tooth sector (2) turn between first end tooth (401) of tooth bar (4) and first time end tooth (402), described linking port (706) is at two drive pin (501) places, when the second end gear teeth (203) of tooth sector (2) depart from the second time end tooth (403) of tooth bar (4), two drive pins (601) are connected port (705) at described two, when the first end gear teeth (202) of tooth sector (2) turn between second end tooth (304) of tooth bar (3) and second time end tooth (303), described linking port (706) is at two drive pin (601) places, if tooth sector (2) is for rotating counterclockwise, when the first end gear teeth (202) of tooth sector (2) depart from the first time end tooth (402) of tooth bar (4)
,two drive pins (501) are connected port (705) at described two, when the first end gear teeth (202) of tooth sector (2) turn between first end tooth (301) of tooth bar (3) and first time end tooth (302), described two are connected port (706) at two drive pin (501) places, when the first end gear teeth (202) of tooth sector (2) depart from the second time end tooth (303) of tooth bar (3), two drive pins (601) are connected port (705) at described two, when the first end gear teeth (202) of tooth sector (2) are between second end tooth (404) and second time end tooth (403) of tooth bar (4), described two are connected port (706) at two drive pin (601) places.
8. according to claim 1, engine-driven gearing described in 7, it is characterized in that: described two turn to groove (703) to be curvilinear groove, two of groove (703) are turned to be connected port (706) place described two driver slots (702) and two, the end of two driver slots (702) and two turn to the end of groove (703) circumscribed, two radiuses turning to the radius of curvature of groove (703) to be greater than two drive pins (501) and two drive pins (601), two turn to two of groove (703) distances be connected between port (706) to main axis (101) to be less than the distance gone out between notch (707) to main axis (101) that two turn to groove (703), if tooth sector (2) is for rotating clockwise, when two turn to groove (703) go out notch (707) and two drive pins (501) depart from time, the first end gear teeth (202) of tooth sector (2) engage with the end tooth (401) of tooth bar (4) and time end tooth (402), when two turn to groove (703) go out notch (707) and two drive pins (601) depart from time, the first end gear teeth (202) of described tooth sector (2) engage with the secondary end tooth (303) of tooth bar (3) and end tooth (304), if tooth sector (2) is for rotating counterclockwise, when two turn to groove (703) go out notch (707) and two drive pins (501) depart from time, the first end gear teeth (202) of tooth sector (2) engage with the end tooth (301) of tooth bar (3) and time end tooth (302), when two turn to groove (703) go out notch (707) and two drive pins (601) depart from time, the first end gear teeth (202) of tooth sector (2) engage with the second time end tooth (403) of tooth bar (4) and the second end tooth (404).
9. the engine-driven gearing according to claim 1-8, is characterized in that: the two end part of described tooth bar (3) and tooth bar (4) connect and compose opposed four cylinder engine group with the piston (12) in four cylinders (13) respectively by connecting rod (11) respectively.
10. the engine-driven gearing according to claim 1-8, it is characterized in that: the main shaft (1) of transmission device of the present invention is connected with the rotating shaft of rotation device (14), the rotary motion of rotation device (14) is converted to the mechanical device of linear reciprocating motion.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201510978706.XA CN105569843A (en) | 2015-12-24 | 2015-12-24 | Engine transmission device for replacing crankshaft-connecting rod mechanism |
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| CN201510978706.XA CN105569843A (en) | 2015-12-24 | 2015-12-24 | Engine transmission device for replacing crankshaft-connecting rod mechanism |
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| CN105569843A true CN105569843A (en) | 2016-05-11 |
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| CN201510978706.XA Pending CN105569843A (en) | 2015-12-24 | 2015-12-24 | Engine transmission device for replacing crankshaft-connecting rod mechanism |
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| CN106996441A (en) * | 2017-05-18 | 2017-08-01 | 郑安庆 | Linear reciprocating motion and rotating movement converting device and air cylinder device |
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| CN110118250A (en) * | 2018-02-05 | 2019-08-13 | 安里千 | A kind of switching mechanism of chain-crankshaft linkage |
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| CN108999698A (en) * | 2018-07-10 | 2018-12-14 | 王刚 | Curved groove transmission shaft type engine |
| CN109139245B (en) * | 2018-09-30 | 2020-11-03 | 安阳工学院 | A crankshaftless engine and its control method |
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| CN109291073A (en) * | 2018-11-02 | 2019-02-01 | 常州大学 | A drive device for discrete rotation of robot two-degree-of-freedom joints |
| CN109291073B (en) * | 2018-11-02 | 2021-10-08 | 常州大学 | A drive device for discrete rotation of robot two-degree-of-freedom joints |
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Application publication date: 20160511 |