CN107725712B - Reciprocating-rotary motion conversion mechanism and water pump thereof - Google Patents
Reciprocating-rotary motion conversion mechanism and water pump thereof Download PDFInfo
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- CN107725712B CN107725712B CN201710826426.6A CN201710826426A CN107725712B CN 107725712 B CN107725712 B CN 107725712B CN 201710826426 A CN201710826426 A CN 201710826426A CN 107725712 B CN107725712 B CN 107725712B
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- 230000007246 mechanism Effects 0.000 title claims abstract description 88
- 238000006243 chemical reaction Methods 0.000 title claims abstract description 26
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 title claims description 43
- 230000001360 synchronised effect Effects 0.000 claims abstract description 16
- 238000010276 construction Methods 0.000 claims 1
- 238000000034 method Methods 0.000 description 14
- 238000010586 diagram Methods 0.000 description 8
- 239000007788 liquid Substances 0.000 description 8
- 238000002485 combustion reaction Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 4
- 210000001503 joint Anatomy 0.000 description 3
- 230000005540 biological transmission Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000007547 defect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000010587 phase diagram Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
Classifications
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/12—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
- F16H37/124—Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types for interconverting rotary motion and reciprocating motion
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- Reciprocating Pumps (AREA)
Abstract
The application discloses a reciprocating-rotary motion conversion mechanism, which comprises a crankshaft, at least three pistons, a machine body and a crankshaft planetary motion driving mechanism, wherein the crankshaft is arranged on the machine body; the crankshaft planetary motion driving mechanism of the gear structure adopts a five-shaft structure. The first shaft is a synchronous shaft, and the first external gear is arranged on the first shaft; the third external gear has the same tooth number and modulus; the first external gear is meshed with the second external gear through a sixth external gear; the reversing shaft provided with the sixth external gear is a third shaft; the second external gear is arranged on a main shaft, and the main shaft is a fourth shaft; the fourth external gear and the eighth external gear are respectively and coaxially and fixedly connected with the machine body through eccentric wheels; the two eccentric wheels are coaxial, and the shaft is a second shaft; the fourth external gear is meshed with the seventh external gear; the eccentric holes of the two eccentric wheels are kept in phase, and the crank journals at the two ends of the crankshaft are rotatably arranged on the eccentric holes. The scheme provided by the application is easy to realize heavy load.
Description
Technical Field
The application relates to a transmission mechanism, in particular to a reciprocating-rotating motion conversion mechanism. The application also provides a water pump using the reciprocating-rotary motion conversion mechanism.
Background
In the patent document with publication number CN1480633A, a technology and a device for realizing long-stroke zero side pressure of a high-heat-efficiency internal combustion engine are proposed, and the device performs planetary motion on an eccentric shaft which is driven to replace a traditional crankshaft through an internally meshed planetary motion gear, so as to further drive a piston connected with the eccentric shaft to perform reciprocating linear motion; the inner gear ring is fixed, the outer gear is meshed with the inner gear ring to do planetary motion, the eccentric shaft is connected with the center of the outer gear in a rotating way, the diameter of the reference circle of the inner gear ring is 2 times of that of the outer gear, and the diameter of the reference circle of the outer gear is 2 times of the eccentric distance of the crankshaft.
The prior art has certain defects that:
1. the technology is applied to the internal combustion engine, because the internal combustion engine only applies work to the outside in a power stroke, and other strokes need to absorb work, the phenomenon that the meshing side is frequently reversed when the planetary gear pair in the mechanism is meshed can be caused, and the phenomenon is similar to the situation that the active and passive gears are frequently changed, and the damage to the planetary gear pair can be caused. Even if the piston is applied to the field of air compressors, the piston can apply work to the eccentric shaft instead of consuming work in the suction stroke due to the pressure of suction gas, and the problem of frequent reversing of the engagement side can be caused. Increasing the number of bellcrank and pistons avoids the problem of reversing, but when the piston phases are required to be evenly arranged, the working direction of some pistons is downward, and for internal combustion engines, the downward arranged pistons often suffer from the significant problem that piston ring lubricating oil easily enters the cylinder to be involved in combustion.
2. Since the diameter of the indexing circle of the external gear which performs planetary motion in the planetary crankshaft transmission mechanism is 2 times of the eccentric distance e of the eccentric shaft, when the diameter of the indexing circle of the gear is increased, the eccentric distance of the eccentric shaft is also increased in a same ratio, and the moment generated by the piston force acting on the eccentric shaft is also increased in the same ratio because of the increase of the eccentric distance of the eccentric shaft, so that the gear can not bear heavy load in a diameter-increasing mode finally. The increase in load carrying capacity by increasing the length of the line of engagement, i.e. increasing the tooth width, is also very limited, since the actual line of engagement is not likely to be too long.
Disclosure of Invention
In order to solve the above problems, the present application provides a reciprocating-rotary motion converting mechanism for a water pump.
The application provides a reciprocating-rotary motion conversion mechanism, which comprises a crankshaft, at least three pistons, a machine body and a crankshaft planetary motion driving mechanism, wherein the crankshaft is arranged on the machine body;
the crankshaft comprises at least two crankshaft journals: a first end crank journal, a second end crank journal and at least three bellcranks, the first end crank journal and the second end crank journal being located at two ends of the crankshaft, respectively;
the at least three pistons are rotatably connected with the at least three bellcrank through connecting rods;
The crankshaft planetary motion driving mechanism of the gear structure adopts a five-shaft structure and is used for ensuring planetary motion of the crankshaft and autorotation of the crankshaft, and the planetary motion of the crankshaft and the autorotation of the crankshaft are combined to enable the piston to do reciprocating linear motion;
the crankshaft planetary motion driving mechanism with the gear structure comprises a first external gear, a second external gear, a third external gear, a fourth external gear, a seventh external gear, an eighth external gear, a fifth external gear, an annular gear, a sixth external gear, a synchronous shaft, a main shaft and a reversing shaft;
the synchronous shaft is a first shaft of the five-shaft structure and is arranged on a machine body through a bearing, and the first external gear, the third external gear and the seventh external gear are arranged on the synchronous shaft; the third external gear and the seventh external gear have the same number of teeth and modulus;
the first external gear is meshed with the second external gear through a sixth external gear; the reversing shaft provided with the sixth external gear is a third shaft of the five-shaft structure; the second external gear is arranged on a main shaft, and the main shaft is a fourth shaft of the five-shaft structure;
the fourth external gear and the eighth external gear have the same specification; the fourth external gear is positioned on the machine body through a first gear eccentric circle which is coaxial and fixedly connected with the fourth external gear, and the eighth external gear is positioned on the machine body through a second gear eccentric circle which is coaxial and fixedly connected with the eighth external gear; the first gear eccentric circle and the second gear eccentric circle are coaxial, the shaft is a second shaft of the five-shaft system, and the second shaft is coaxial with the fourth shaft; the fourth external gear is meshed with the third external gear, and the seventh external gear is meshed with the eighth external gear; the eccentric holes of the first gear eccentric circle and the second gear eccentric circle are kept in phase, the first end crank journal of the crankshaft is rotatably installed on the eccentric hole of the first gear eccentric circle, namely a first crankshaft connecting hole, the second end crank journal is rotatably installed on the eccentric hole of the second gear eccentric circle, namely a second crankshaft connecting hole, and the axes of the first end crank journal and the second end crank journal are the fifth shaft of the five-shaft system;
The third external gear and the fourth external gear are meshed, and the seventh external gear and the eighth external gear are meshed; the fifth external gear is mounted on the fourth shaft and is positioned outside the bearing; an inner gear ring meshed with the fifth outer gear is arranged on a fifth shaft; the engaged fifth external gear and ring gear may be interchanged; after interchange, the inner gear ring is mounted on the main shaft, and the fifth outer gear is mounted on a fifth shaft which is the first end crank journal of the crankshaft;
the above-mentioned indexing circle diameter of external gear and annular gear meets the following formula at the same time:
d 33 +2e＝d 33’
wherein d 31 The reference circle diameter is the reference circle diameter of the first external gear; d, d 31’ The reference circle of the second external gear is directly lowered; d, d 32 The reference circle diameter of the third external gear; d, d 32’ A pitch circle diameter for the fourth outer gear; d, d 33 The reference circle diameter of the fifth external gear; d, d 33’ Is the indexing circle diameter of the inner gear ring;
the machine body is used for installing the piston and the crankshaft planetary motion driving mechanism; the at least three pistons are arranged in a reciprocating motion track of the machine body, and the axis of the reciprocating motion track is perpendicular to the main shaft.
Preferably, the piston is a single-acting piston.
Preferably, the number of pistons is the same as the number of throws of the crankshaft, one of the pistons being connected to one of the throws.
Preferably, the included angle between any two bellcrank of the crankshaft is 2 times of the included angle between two pistons connected with the crankshaft.
Preferably, the projections of the crank throws of the crankshaft on a plane perpendicular to the central line of the crankshaft are uniformly distributed circumferentially with the projections of the central line of the crankshaft as circle centers.
Preferably, the number of the bell crank and the number of the pistons are singular.
Preferably, the single bell crank has the following arrangement order in the axial direction of the crankshaft: the projections of crank pins corresponding to each crank throw which is sequentially arranged in the axial direction on a plane perpendicular to the central line of the crankshaft are sequentially and uniformly distributed along one rotation direction of the circumference; correspondingly, the included angles between any two adjacent projections of the pistons perpendicular to the central line of the crankshaft are equal.
Preferably, the number of the crank throws and the number of the pistons are 3, 5, 7, 9 and 11 respectively.
Preferably, when the number of the bellcrank and the number of the pistons are 3, the phase angles of the 3 bellcrank are 0 °, 240 °, 480 °, and the phase angles of the 3 pistons connected with the corresponding bellcrank are 0 °, 120 °, 240 °;
Preferably, when the number of the bellcrank and the number of the pistons are both 5, the phase angles of the 5 bellcrank are 0 °, 144 °, 288 °, 432 °, 576 °, and the phase angles of the 5 pistons connected to the bellcrank are 0 °, 72 °, 144 °, 216 °, 288 °;
preferably, when the number of the bellcrank and the number of the pistons are both 7, the phase angles of the 7 bellcrank are 0 °, 102.857 °, 205.714 °, 308.571 °, 411.429 °, 514.286 °, 617.143 °, and the phase angles of the 7 pistons connected thereto are 0 °, 51.429 °, 102.857 °, 154.286 °, 205.714 °, 257.143 °, 308.571 °;
preferably, when the number of the bellcrank and the number of the pistons are both 9, the phase angles of the 9 bellcrank are 0 °, 80 °, 160 °, 240 °, 320 °, 400 °, 480 °, 560 °, 640 °, and the phase angles of the 9 pistons connected thereto are 0 °, 40 °, 80 °, 120 °, 160 °, 200 °, 240 °, 280 °, 320 °;
preferably, when the number of the bellcrank and the number of the pistons are 11, the phase angles of the 11 bellcrank are 0 °, 65.455 °, 130.909 °, 196.364 °, 261.818 °, 327.273 °, 392.727 °, 458.182 °, 523.636 °, 589.091 °, 654.545 °, and the phase angles of the 11 pistons connected thereto are 0 °, 32.727 °, 65.455 °, 98.182 °, 130.909 °, 163.636 °, 196.364 °, 229.091 °, 261.818 °, 294.545 °, 327.273 °;
Preferably, the number of the crank throw and the number of the pistons are two or more.
Preferably, the number of the bell cranks and the number of the pistons are 6.
Preferably, when the number of the bell cranks and the number of the pistons are both 6, the phase angles of the 6 bell cranks are 0 °, 180 °, 240 °, 420 °, 480 °, 660 °, and the phase angles of the 6 pistons connected thereto are 0 °, 90 °, 120 °, 210 °, 240 °, 330 °.
Preferably, the crankshaft may further comprise a single or a plurality of intermediate journals in addition to the first and second end journals, the single or plurality of intermediate journals being located between two of the crankshafts; correspondingly, an intermediate crank journal eccentric circle is arranged, an intermediate crank journal eccentric hole with the eccentric distance of e is formed in the intermediate crank journal eccentric circle, the single or a plurality of intermediate crank journals penetrate through the intermediate crank journal eccentric hole on the intermediate crank journal eccentric circle, and the intermediate crank journal eccentric circle and the machine body are rotatably mounted together.
Preferably, the eccentric circle of the middle crank journal is of a split structure, and the eccentric hole of the middle crank journal is formed by butt joint of arc holes respectively positioned at the split parts.
Preferably, the part of the synchronizing shaft extending out of the machine body is used as a power input shaft, and a mechanical structure used as the power input shaft is arranged on the extending part.
Preferably, a portion of the synchronizing shaft, which is adjacent to the gear and protrudes from the body, is used as a power input shaft.
Preferably, the part of the main shaft extending out of the machine body is used as a power input shaft, and a mechanical structure used as the power input shaft is arranged on the extending part.
Preferably, the crank arm of the crankshaft includes a counterweight structure thereon.
The application also provides a water pump, which uses the reciprocating-rotary motion conversion mechanism according to any one of the technical schemes.
Compared with the prior art, the application has the following characteristics:
1. in the application, the pitch circle diameter of two gears in the internally meshed planetary motion gear pair is far larger than 2 times of the eccentric distance e of the crankshaft, and the pitch circle diameter of an external gear in the internally meshed planetary motion gear pair in the prior art is equal to 2 times of the eccentric distance e of the eccentric shaft.
2. In the application, the inner gear ring of the internally meshed planetary motion gear pair rotates, and the inner gear ring of the internally meshed planetary motion gear pair in the prior art is fixed; therefore, the gear which performs planetary motion in the application can be any gear in the internally meshed planetary motion gear pair, namely, the external gear or the annular gear can be fixed together with the crankshaft to perform planetary motion, and only the external gear in the internally meshed planetary motion gear pair in the prior art can perform planetary motion;
3. The application field of the invention is the field of liquid working media such as water pumps, and is different from gas working media of internal combustion engines and air compressors. The main difference is that the sealing mode is that the water pump has no piston ring, and the piston can be arranged downwards. The problem of planet gear mesh side commutation can thus be avoided by arranging a plurality of pistons.
In summary, the invention has the following advantages:
1. the pitch circle diameter of two gears in the internally meshed planetary motion gear pair in the crankshaft planetary motion driving mechanism of the gear structure is far greater than 2 times of the crankshaft eccentric distance e, so that the limitation of the eccentric shaft eccentric distance e with the pitch circle diameter equal to 2 times of the external gear in the internally meshed planetary motion gear pair in the prior art is broken through, the heavy load can be realized, and the load capacity of the whole reciprocating-rotating motion conversion mechanism for the water pump is greatly improved, so that the heavy load is easy to realize;
2. the gear which performs planetary motion can be any gear in an internally meshed planetary motion gear pair, namely, the external gear or the annular gear can be fixed together with the crankshaft to perform planetary motion, so that the mechanism is more flexible in use;
3. The application can be mainly applied to the field of liquid working mediums such as water pumps, and the like, and the problem of reversing the meshing side of the planetary gear can be avoided by arranging a plurality of pistons, namely the phenomenon of gear collision is effectively avoided, and the service life of the reciprocating-rotary motion conversion mechanism is prolonged; the application is especially suitable for water pumps, and can also be used in occasions such as compressors, engines and the like;
4. the number of pistons of the present application can be relatively large, so that the reciprocating-rotary motion converting mechanism for a water pump can obtain a small pulsation rate.
Drawings
FIG. 1 is a three-dimensional schematic view of a 6-piston reciprocating-rotary motion conversion mechanism for a water pump according to an embodiment of the present application
FIG. 2 is a schematic diagram of a 6-throw crankshaft in accordance with an embodiment of the present application
FIG. 3 is a schematic diagram of a 9-throw crankshaft in accordance with an embodiment of the present application
FIG. 4 is a schematic diagram of piston phases of a 3-piston reciprocating-rotary motion conversion mechanism for a water pump according to an embodiment of the present application
FIG. 5 is a perspective view of a 6-piston reciprocating-rotary motion converting mechanism for a water pump according to an embodiment of the present application, with a body removed, on a plane perpendicular to the center line of a crankshaft
FIG. 6 is a three-dimensional schematic view of a 6-piston reciprocating-rotary motion conversion mechanism for a water pump according to an embodiment of the present application with a body removed
FIG. 7 is a schematic diagram of a 3-piston reciprocating-rotary motion conversion mechanism for a water pump according to an embodiment of the present application
FIG. 8 is a two-dimensional schematic view of a 3-piston reciprocating-rotary motion converting mechanism for a water pump according to an embodiment of the present application with a body removed
FIG. 9 is a schematic structural view of a second gear eccentric circle according to an embodiment of the present application
FIG. 10 is a schematic structural view of an intermediate crank journal eccentric in accordance with an embodiment of the present application
In fig. 1-10, the relevant reference numerals are as follows:
the crankshaft 1, the piston 2, the crankshaft planetary motion guaranteeing mechanism 3 of the gear structure, the machine body 4, the connecting rod 5, the first gear eccentric circle 6, the second gear eccentric circle 6', the middle crank journal eccentric circle 7;
a first end crank journal 11, a second end crank journal 12, a bell crank 13, an intermediate crank journal 14;
crank arm 131 and crank pin 132;
a first external gear 31, a second external gear 31', a third external gear 32, a fourth external gear 32', a fifth external gear 33, an inner gear ring 33', a sixth external gear 33, a synchronizing shaft 35, a main shaft 36, a seventh external gear 38, an eighth external gear 38', a reversing shaft 37;
A first center hole 311; a second central aperture 321; a third central aperture 31'1; a fourth center hole 331; a fifth central aperture 33'1; a center 32'1, a first crankshaft connecting hole 32'2; a sixth central bore 381; a second crankshaft connecting hole 38'1;
a reciprocating rail 41, a synchronizing shaft support hole 42, a main shaft support hole 43, a reversing shaft support hole 44;
the middle crank journal eccentric hole 71 and the middle crank journal eccentric circle connecting screw 72.
Detailed Description
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present application. The present application may be embodied in many other forms than those herein described, and those skilled in the art will readily appreciate that the present application may be similarly embodied without departing from the spirit or essential characteristics thereof, and therefore the present application is not limited to the specific embodiments disclosed below.
Referring to fig. 1, fig. 1 is a three-dimensional schematic view of a reciprocating-rotary motion converting mechanism for a water pump according to an embodiment of the present application. It should be noted that, the structure of the reciprocating-rotary motion converting mechanism for a water pump will be described herein by taking only the case where the number of pistons is six as an example, and in fact, the number of pistons of the reciprocating-rotary motion converting mechanism for a water pump is not limited to six, and reference will be made to the following related matters for a specific description of the number of pistons.
As shown in fig. 1, the six-piston reciprocating-rotary motion conversion mechanism for a water pump comprises a crankshaft 1, a single-acting piston 2, a crankshaft planetary motion assurance mechanism 3 of a gear structure, and a machine body 4.
The crankshaft planetary motion driving mechanism 3 with the gear structure is used for ensuring that the crankshaft 1 performs planetary motion, and the planetary motion of the crankshaft 1 drives the piston 2 to perform reciprocating linear motion.
The single-acting piston 2 and the crank planetary motion driving mechanism 3 with a gear structure are arranged in the machine body 4.
Referring to fig. 2 and 3, fig. 2 is a schematic diagram of a six-throw crankshaft according to an embodiment of the present application, and fig. 3 is a schematic diagram of a nine-throw crankshaft according to an embodiment of the present application.
As shown in fig. 2 and 3, the crankshaft 1 includes at least two crank pins: a first end crank journal 11, a second end crank journal 12 and at least three crank throws 13, said first end crank journal 11 and second end crank journal 12 being located at the two ends of said crankshaft 1, respectively.
The bell crank 13 includes two crank arms 131 and a crank pin 132 connecting the two crank arms 131.
As shown in fig. 3, when the length of the crankshaft 1 is excessively long, a single or a plurality of intermediate journals 14 may be added to enhance the fracture resistance thereof. The intermediate crank journal 14 is located between the two bell cranks 13 of the crankshaft 1.
The number of said throws 13 of said crankshaft 1 may be singular of at least 3 to obtain a small liquid pulse rate. The number of the liquid pulses may be two or more, and when the number of the liquid pulses is two or more, 6 are special cases, and a smaller liquid pulse rate may be obtained, and when the number of the liquid pulses is two or more, the liquid pulse rate is relatively large. When the number of bell cranks 13 is singular, the pistons 2 are also singular of the same number. As shown in fig. 3, the single bell crank 13 has the following arrangement order in the axial direction of the crankshaft 1: the projections of the crank pins 132 corresponding to the respective bellcranks 13 arranged in sequence in the axial direction on a plane perpendicular to the center line of the crankshaft 1 are arranged uniformly in one rotation direction of the circumference;
when the number of the bell cranks 13 is a double number of 6, as shown in fig. 2, the arrangement order of the double number of bell cranks 13 in the axial direction of the crankshaft 1 cannot have the above-described rule.
In order to ensure smooth rotation of the crankshaft 1 to reduce vibration, a weight structure is further provided on the crank arm 131 of the bell crank 13 of the crankshaft 1.
The number of the single-acting pistons 2 is the same as the number of the bell cranks 13, so that the reciprocation-rotation motion converting mechanism for a water pump includes at least 3 pistons 2. As shown in fig. 6, which is a three-dimensional schematic view of a six-piston reciprocating-rotary motion converting mechanism for a water pump according to an embodiment of the present application, each of the single-acting pistons 2 is rotatably coupled to each of the bell cranks 13 by a connecting rod 5.
The phase angle of any one of the bell cranks 13 of the crankshaft 1 is 2 times the phase angle of the piston 2 connected thereto. The phase angle refers to the relative angle of any bell crank and its corresponding piston projected in the circumferential direction on a plane perpendicular to the center line of the crankshaft 1.
The following describes the single number of the bell cranks 13 and the pistons 2, which are 3, 5, 7, 9, 11, respectively, and the phase angles of the bell cranks 13 and the pistons 2 when the number of the bell cranks 13 and the pistons 2 is a double number of 6; the following table can be referred to simultaneously.
As shown, when the number of the bell cranks 13 and the pistons 2 is 3, the phase angles of 3 of the bell cranks 13 are 0 °, 240 °, 480 °, and correspondingly, the phase angles of 3 of the pistons 2 connected thereto are 0 °, 120 °, 240 °.
When the number of the bell cranks 13 and the pistons is 5, the phase angles of 5 bell cranks 13 are 0 °, 144 °, 288 °, 432 °, 576 °, and correspondingly, the phase angles of 5 pistons 2 connected thereto are 0 °, 72 °, 144 °, 216 °, 288 °.
When the number of the bell cranks 13 and the number of the pistons 2 are 7, the phase angles of 7 bell cranks 13 are 0 °, 102.857 °, 205.714 °, 308.571 °, 411.429 °, 514.286 °, 617.143 °, and the phase angles of 7 pistons 2 connected thereto are 0 °, 51.429 °, 102.857 °, 154.286 °, 205.714 °, 257.143 °, 308.571 °.
When the number of the bell cranks 13 and the number of the pistons 2 are 9, the phase angles of the 9 bell cranks 13 are 0 °, 80 °, 160 °, 240 °, 320 °, 400 °, 480 °, 560 °, 640 °, and the phase angles of the 9 pistons 2 connected thereto are 0 °, 40 °, 80 °, 120 °, 160 °, 200 °, 240 °, 280 °, 320 °.
When the number of the bell cranks 13 and the pistons 2 is 11, the phase angles of 11 bell cranks (13) are 0 °, 65.455 °, 130.909 °, 196.364 °, 261.818 °, 327.273 °, 392.727 °, 458.182 °, 523.636 °, 589.091 °, 654.545 °, and correspondingly, the phase angles of 11 pistons 2 connected thereto are 0 °, 32.727 °, 65.455 °, 98.182 °, 130.909 °, 163.636 °, 196.364 °, 229.091 °, 261.818 °, 294.545 °, 327.273 °.
It can be seen that when the number of bellcrank 13 and the number of pistons 2 are singular, the angles between any two adjacent projections of the pistons 2 on the plane perpendicular to the center line of the crankshaft 1 are equal. As shown in fig. 4, which is a piston phase diagram of a 3-piston reciprocating-rotary motion conversion mechanism for a water pump according to an embodiment of the present application, the angle between any two adjacent projections of three single-acting pistons 2 on the plane perpendicular to the center line of the crankshaft 1 is 120 °.
When the number of the bell cranks 13 and the number of the pistons 2 are 6, the phase angles of the 6 bell cranks 13 are 0 °, 180 °, 240 °, 420 °, 480 °, 660 °, and the phase angles of the 6 pistons 2 connected thereto are 0 °, 90 °, 120 °, 210 °, 240 °, 330 °.
It can be seen that when the number of bellcrank 13 and piston 2 is 6, the angle between any two adjacent projections of piston 2 on the plane perpendicular to the center line of crankshaft 1 is not exactly equal. As shown in fig. 5, which is a projection view of the 6 pistons of the reciprocating-rotary motion converting mechanism for a water pump according to the embodiment of the present application, on a plane perpendicular to the center line of the crankshaft, after the body is removed, the angle between any two adjacent projections of the 6 single-acting pistons 2 on the plane perpendicular to the center line of the crankshaft 1 is not exactly equal, and is 30 ° or 90 °.
For the structure of the crank planetary motion assurance mechanism 3 of the gear structure, please refer to fig. 6 and fig. 7, 8.
Fig. 7 is a schematic diagram of a 3-piston reciprocating-rotary motion conversion mechanism for a water pump according to an embodiment of the present application.
Fig. 8 is a two-dimensional schematic view of a 3-piston reciprocation-rotation motion conversion mechanism for a water pump according to an embodiment of the present application.
As described above, fig. 6, 7 and 8 will be described by taking only 6 and 3 pistons as examples, and reference is made to the foregoing for specific description of the number of pistons.
As shown in fig. 6, 7 and 8, the crankshaft planetary motion driving mechanism 3 adopts a five-axis structure, and is used for ensuring the planetary motion of the crankshaft 1 and the rotation of the crankshaft 1; the crank planetary motion driving mechanism 3 includes a first external gear 31, a second external gear 31', a third external gear 32, a fourth external gear 32', a fifth external gear 33, an annular gear 33', a sixth external gear 33, a synchronization shaft 35, a main shaft 36, a reverse shaft 37, a seventh external gear 38, and an eighth external gear 38'. The structure of the crank planetary motion driving mechanism 3 will be described in detail below with reference to the drawings.
As shown in the drawing, the synchronizing shaft 35 is a first shaft of the five-shaft mechanism, the synchronizing shaft 35 is mounted on a machine body through bearings, and the first external gear 31, the third external gear 32 and the seventh external gear 38 are respectively provided with a first central hole 311, a second central hole 321 and a sixth central hole 381, through which the three external gears are fixedly mounted on the synchronizing shaft 35 to rotate with the rotation of the synchronizing shaft; the third external gear 32 and the seventh external gear 38 have the same number of teeth and modulus.
The first external gear 31 is meshed with the second external gear 31' through a sixth external gear 33; a reversing shaft (37) for mounting the sixth external gear (34) is a third shaft of the five-shaft structure; the second external gear 31' is provided with a third central hole 31'1, and is fixedly connected with the main shaft 36 through the third central hole 31'1, and the main shaft 36 is a fourth shaft of the five-shaft structure. The method comprises the steps of carrying out a first treatment on the surface of the
The fourth external gear (32 ') and the eighth external gear (38') have the same specifications; the fourth external gear (32 ') is seated on the machine body through a first gear eccentric circle (6) which is coaxial and fixedly connected with the fourth external gear, and the eighth external gear (38 ') is seated on the machine body through a second gear eccentric circle (6 ') which is coaxial and fixedly connected with the eighth external gear; the first gear eccentric circle (6) and the second gear eccentric circle (6') are coaxial, the shaft is a second shaft of the five-shaft system, and the second shaft is coaxial with the fourth shaft; the fourth external gear (32 ') meshes with the third external gear (32), and the eighth external gear (38') meshes with the seventh external gear (38); the eccentric holes of the first gear eccentric circle (6) and the second gear eccentric circle (6 ') are kept in phase, the first end crank journal (11) of the crankshaft (1) is rotatably mounted on the eccentric hole of the first gear eccentric circle (6), namely a first crankshaft connecting hole (32' 2), the second end crank journal (12) is rotatably mounted on the eccentric hole of the second gear eccentric circle (6 '), namely a second crankshaft connecting hole (38' 1), and the axes of the first end crank journal (11) and the second end crank journal (12) are fifth axes of the five-axis system.
The fifth external gear 33 and the ring gear 33' are positioned between the second external gear 31' and the fourth external gear 32', the fifth external gear 33 and the ring gear 33' are meshed, and a fourth center hole 331 and a fifth center hole 33'1 are respectively opened; the fourth central hole 331 is fixedly connected with the main shaft 36; the fifth central bore 33'1 is fixedly connected to the first end crankshaft journal 11 of the crankshaft 1;
in terms of component manufacturing, the first gear eccentric circle 6 may be mounted on the fourth external gear 32 'as a separate structure, or may be integrated with the fourth external gear 32'. Similarly, the second gear eccentric circle 6' may be mounted on the eighth external gear 38' as a separate structure, or may be integrated with the eighth external gear 38 '.
The above-mentioned indexing circle diameters of the external gear and the internal gear ring simultaneously satisfy the following formulas:
d 33 +2e＝d 33’
the labels in the above formulas are defined as: d, d 31 A pitch circle diameter of the first external gear 31; d, d 31’ A pitch circle diameter for the second external gear 31'; d, d 32 A pitch circle diameter for the third external gear 32; d, d 32’ A pitch circle diameter for the fourth outer gear 32'; d, d 33 A pitch circle diameter of the fifth external gear 33; d, d 33’ Is the pitch diameter of the inner and outer ring gears 33'.
The fifth external gear 33 and the ring gear 33' which are engaged with each other in the crank planetary motion driving mechanism 3 of the gear structure may be interchanged without affecting the function of the crank planetary motion driving mechanism 3 of the gear structure. After interchange, the fifth central hole 33'1 of the ring gear 33' is fixedly connected with the main shaft 36; the fourth center hole 331 of the fifth external gear 33 is fixedly connected to the first end crank pin 11 of the crankshaft 1, while the formulas that the gear structure of the crankshaft planetary motion driving mechanism 3 needs to satisfy, as well as other elements and their connection relationship, remain unchanged.
Returning to fig. 1, the machine body 4 is provided with reciprocating rails 41 corresponding to the number of the pistons 2 at positions corresponding to the pistons 2, the axial direction of the reciprocating rails 41 is perpendicular to the main shaft 36, and the at least three pistons 2 are respectively arranged in the reciprocating rails 41 in a one-to-one correspondence.
The front and rear end covers of the machine body 4 are respectively provided with a synchronous shaft supporting hole 42 corresponding to the synchronous shaft 35 for fixing the synchronous shaft 35; the front end cover of the machine body 4 is further provided with a main shaft supporting hole 43 and a reversing shaft supporting hole 44 at positions corresponding to the main shaft 36 and the reversing shaft 37, respectively, for fixing the main shaft 36 and the reversing shaft 37, respectively.
The first end crank pin 11 of the crankshaft 1 is disposed in the first crankshaft connecting hole 32'2 having the eccentricity e of the first gear eccentric circle 6, and the second end crank pin 12 of the crankshaft 1 is disposed in the second crankshaft connecting hole 38'1 having the eccentricity e of the second gear eccentric circle 6 '. Please refer to fig. 9, which is a schematic diagram of the structure of the second gear eccentric circle, wherein the structure of the first gear eccentric circle 6 is the same as that of the second gear eccentric circle 6'. As shown in fig. 6, the first gear eccentric circle 6 and the second gear eccentric circle 6' are formed as a single body and are mounted by being respectively fitted around the first end crank pin 11 and the second end crank pin 12.
When the crankshaft 1 is provided with the intermediate crank journal 14, it is also necessary to provide an intermediate crank journal eccentric circle 7, as shown in fig. 10, which is a schematic view of the structure of the intermediate crank journal eccentric circle. The eccentric circle of the middle crank journal is provided with a middle crank journal eccentric hole 71 with the eccentric distance e, the middle crank journal 14 passes through the middle crank journal eccentric hole 71, and the middle crank journal eccentric circle 7 and the machine body 4 are rotatably arranged together.
And in order to facilitate the installation, the eccentric circle 7 of the middle crank journal is of an upper and lower split structure, the eccentric hole 71 of the middle crank journal is formed by butt joint of arc holes respectively positioned on the upper split part and the lower split part, and the upper split part and the lower split part are fixedly connected together by using the eccentric circle connecting screw 72 of the middle crank journal during the installation.
When the reciprocating-rotating motion converting mechanism for the water pump is operated, the reciprocating motion of the piston 2 can be converted into the rotating motion of the main shaft 36 and the synchronizing shaft 35, and the rotating motion of the main shaft 36 and the synchronizing shaft 35 can also be converted into the reciprocating motion of the piston 2, and the specific working process is as follows:
when the rotary motion of the main shaft 36 and/or the synchronizing shaft 35 is converted into the reciprocating motion of the piston 2, the main shaft 36 and/or the synchronizing shaft 35 performs rotary motion to drive the second external gears 31' and 31 to rotate; and the second external gear 31' drives the fifth external gear 33 to rotate, and then drives the ring gear 33' to rotate, and then drives the first end crank pin 11 and the second end crank pin 12 of the crankshaft 1 to rotate in the first crankshaft connecting hole 32'2 and the second crankshaft connecting hole 38'1 of the fourth external gear 32', and simultaneously, the first external gear 31 drives the third external gears 32 and 38 to rotate, and then drives the fourth external gear 32' meshed with the third external gear 32 and the gear 38' meshed with the gear 38 to synchronously rotate, so that the first end crank pin 11 and the second end crank pin 12 of the crankshaft 1 are driven to revolve around the main shaft 36, and the crankshaft 1 is ensured to do planetary motion.
Due to the fact that the pitch circle diameter of the first external gear 31 is d 31 The method comprises the steps of carrying out a first treatment on the surface of the The second external gear 31' has a pitch circle diameter d 31’ The method comprises the steps of carrying out a first treatment on the surface of the The third external gear 32 has a pitch diameter d 32 The method comprises the steps of carrying out a first treatment on the surface of the The fourth outer gear 32' has a pitch circle diameter d 32’ The method comprises the steps of carrying out a first treatment on the surface of the The fifth external gear 33 has a pitch diameter d 33 The method comprises the steps of carrying out a first treatment on the surface of the The pitch diameter of the ring gear 33' is d 33’ Simultaneously satisfies:
d 33 +2e＝d 33’
and further, it is ensured that the planetary motion of the crankshaft 1 can drive 6 bell cranks 13 to reciprocate linearly, and finally drive 6 pistons 2 to reciprocate respectively.
When the reciprocating motion of the piston 2 is converted into the rotary motion of the main shaft 36 and the synchronizing shaft 35, 6 pistons 2 respectively reciprocate in 6 reciprocating motion tracks 41 of the machine body 4, respectively drive 6 crank throws 13 of the crankshaft 1 rotatably connected with the pistons to do linear motion, drive the first end crank journal 11 and the second end crank journal 12 of the crankshaft 1 to do regular synchronous planetary motion, and the first end crank journal 11 rotates to drive the inner gear ring 33 'fixedly connected with the first end crank journal to rotate, further drive the fifth outer gear 33 meshed with the inner gear ring 33' to rotate, further drive the main shaft 36 and the second outer gear 31 'to rotate, further drive the first outer gear 31 meshed with the second outer gear 31' through the sixth outer gear 33, and further drive the synchronizing shaft 35 fixedly connected with the first outer gear 31 to rotate; at the same time, the revolution of the first end crank shaft 11 and the second end crank shaft 12 drives the fourth external gears 32 'and 38' to rotate, and thus drives the third external gear 32 meshed with the fourth external gear 32 'and the seventh external gear 38 meshed with the eighth external gear 38' to synchronously rotate, and thus drives the synchronizing shaft 35 fixedly connected thereto to rotate, and the rotation of the synchronizing shaft 35 drives the first external gear 31 fixedly connected thereto to rotate, and thus drives the second external gear 31 'meshed with the first external gear 31 through the sixth external gear 33 to rotate, and thus drives the spindle 36 fixedly connected with the second external gear 31' to rotate.
Due to the fact that the pitch circle diameter of the first external gear 31 is d 31 The method comprises the steps of carrying out a first treatment on the surface of the The second external gear 31' has a pitch circle diameter d 31’ The method comprises the steps of carrying out a first treatment on the surface of the The third external gear 32 has a pitch diameter d 32 The method comprises the steps of carrying out a first treatment on the surface of the The fourth outer gear 32' has a pitch circle diameter d 32’ The method comprises the steps of carrying out a first treatment on the surface of the The fifth external gear 33 has a pitch diameter d 33 The method comprises the steps of carrying out a first treatment on the surface of the The pitch diameter of the ring gear 33' is d 33’ Simultaneously satisfies:
d 33 +2e＝d 33’
the crankshaft 1 is restricted from regular planetary motion, ensuring smooth operation of the reciprocating-rotating motion mechanism.
Furthermore, the pitch diameter of the ring gear 33' fixedly connected to the crankshaft in the reciprocating rotary motion mechanism also satisfies d 33’ >2e, breaking through the limitation of the eccentric distance e of the eccentric shaft with the reference circle diameter equal to 2 times of the external gear fixedly connected with the crankshaft in the internally meshed planetary motion gear pair in the prior art, the heavy load can be realized, and the load capacity of the whole reciprocating-rotating motion conversion mechanism for the water pump is greatly improved.
It should be noted that, the synchronizing shaft 35 and/or the main shaft 36 may be used as a power input shaft of the reciprocating-rotary motion conversion mechanism for a water pump, and the specific implementation method is as follows: the shaft 35 and/or the main shaft 36 are/is provided with a coupling on the protruding part protruding out of the machine body 4, and the motor can be connected through the coupling to provide power input for the reciprocating-rotating motion conversion mechanism for the water pump.
Since most parts of the reciprocating-rotary motion converting mechanism are located on the left side of the crankshaft 1, for maintenance, it is more preferable to use the portion of the synchronizing shaft 35 extending out of the machine body, which is close to the gear 38, as a power input shaft, and the detailed implementation method is the same as above, and will not be repeated here.
The reciprocating-rotating motion converting mechanism provided in the above embodiment adopts a horizontal structure in which each shaft of the five-shaft structure is parallel to the ground, but in fact, the reciprocating-rotating motion converting mechanism may also adopt a vertical structure in which each shaft is perpendicular to the bottom surface, but when adopting the vertical structure, it is necessary to ensure that each bearing can bear axial force; this technical effect can be achieved using a thrust bearing.
The present application also protects a water pump using the reciprocating-rotary motion converting mechanism of the above-described embodiment, and can obtain the advantageous effects of the reciprocating-rotary motion converting mechanism for a water pump of the above-described embodiment. The assembly of the reciprocating-rotary motion conversion mechanism for the water pump and other related parts of the water pump can be referred to the prior art, and will not be repeated here.
The present application also protects an engine using the reciprocating-rotary motion converting mechanism of the above embodiment, and can obtain the advantageous effects of the reciprocating-rotary motion converting mechanism for a water pump of the above embodiment. The assembly of the reciprocating-rotary motion conversion mechanism for the water pump and other related parts of the water pump can be referred to the prior art, and will not be repeated here.
The present application also protects an air compressor using the reciprocating-rotary motion converting mechanism of the above embodiment, and can obtain the advantageous effects of the reciprocating-rotary motion converting mechanism for a water pump of the above embodiment. The assembly of the reciprocating-rotary motion conversion mechanism for the water pump and other related parts of the water pump can be referred to the prior art, and will not be repeated here.
1. The reciprocating-rotary motion conversion mechanism comprises a crankshaft (1), at least three pistons (2) and a machine body, and is characterized by further comprising a crankshaft planetary motion driving mechanism (3);
the crankshaft (1) comprises at least two crank journals: a first end crank journal (11), a second end crank journal (12) and at least three bellcrank (13), the first end crank journal (11) and the second end crank journal (12) being located at both ends of the crankshaft (1), respectively;
the at least three pistons (2) are rotatably connected with the at least three bellcrank by connecting rods;
the crankshaft planetary motion driving mechanism (3) of the gear structure adopts a five-shaft structure and is used for ensuring the planetary motion of the crankshaft (1) and the autorotation of the crankshaft (1), and the planetary motion of the crankshaft (1) and the autorotation of the crankshaft (1) are combined to enable the piston (2) to do reciprocating linear motion;
The crankshaft planetary motion driving mechanism (3) with the gear structure comprises a first external gear (31), a second external gear (31 '), a third external gear (32), a fourth external gear (32'), a seventh external gear (38), an eighth external gear (38 '), a fifth external gear (33), an annular gear (33'), a sixth external gear (34), a synchronous shaft (35), a main shaft (36) and a reversing shaft (37);
the synchronous shaft (35) is a first shaft of the five-shaft structure, the synchronous shaft (35) is arranged on a machine body through a bearing, and the first external gear (31), the third external gear (32) and the seventh external gear (38) are arranged on the synchronous shaft (35); the third external gear (32) and the seventh external gear (38) have the same number of teeth and modulus;
the first external gear (31) is meshed with the second external gear (31') through a sixth external gear (34); a reversing shaft (37) for mounting the sixth external gear (34) is a third shaft of the five-shaft structure; the second external gear (31') is arranged on a main shaft (36), and the main shaft (36) is a fourth shaft of the five-shaft structure;
the fourth external gear (32 ') and the eighth external gear (38') have the same specifications; the fourth external gear (32 ') is seated on the machine body through a first gear eccentric circle (6) which is coaxial and fixedly connected with the fourth external gear, and the eighth external gear (38 ') is seated on the machine body through a second gear eccentric circle (6 ') which is coaxial and fixedly connected with the eighth external gear; the first gear eccentric circle (6) and the second gear eccentric circle (6') are coaxial, the shaft is a second shaft of the five-shaft system, and the second shaft is coaxial with the fourth shaft; the fourth external gear (32 ') meshes with the third external gear (32), and the seventh external gear (38) meshes with the eighth external gear (38'); the eccentric holes of the first gear eccentric circle (6) and the second gear eccentric circle (6 ') are kept in phase, the first end crank journal (11) of the crankshaft (1) is rotatably mounted on the eccentric hole of the first gear eccentric circle (6), namely a first crankshaft connecting hole (32' 2), the second end crank journal (12) is rotatably mounted on the eccentric hole of the second gear eccentric circle (6 '), namely a second crankshaft connecting hole (38' 1), and the axes of the first end crank journal (11) and the second end crank journal (12) are fifth axes of the five-axis system;
The third external gear (32) and the fourth external gear (32 ') are meshed, and the seventh external gear (38) and the eighth external gear (38') are meshed; the fifth external gear (33) is mounted on the fourth shaft and is positioned outside the bearing; an inner gear ring (33') meshed with the fifth outer gear (33) is mounted on the fifth shaft; -the meshed fifth external gear (33) and ring gear (33') are interchangeable; after interchange, the inner gear ring (33') is mounted on the main shaft (36), and the fifth outer gear (33) is mounted on the first end journal (11), i.e., a fifth shaft, of the crankshaft (1);
the above-mentioned indexing circle diameter of external gear and annular gear meets the following formula at the same time:
d 33 +2e＝d 33’
wherein d 31 Is the pitch circle diameter of the first external gear (31); d, d 31’ The pitch circle for the second external gear (31') is lowered straight; d, d 32 Is the pitch circle diameter of the third external gear (32); d, d 32’ A pitch circle diameter for a fourth external gear (32'); d, d 33 Is the pitch circle diameter of the fifth external gear (33); d, d 33’ Is the pitch circle diameter of the inner gear ring (33');
the machine body is used for mounting the piston (2) and the crankshaft planetary motion driving mechanism (3); the at least three pistons (2) are arranged in a reciprocating track of the machine body, the axis of the reciprocating track being perpendicular to the main shaft (36).
Optionally, the piston (2) is a single-acting piston.
Optionally, the number of pistons (2) is the same as the number of bellcrank throws (13) of the crankshaft (1), one piston (2) being connected to each bellcrank (13).
Optionally, the included angle between any two bellcrank (13) of the crankshaft (1) is 2 times that between two pistons (2) connected with the crankshaft.
Optionally, the projections of the bellcrank (13) of the crankshaft (1) on a plane perpendicular to the center line of the crankshaft (1) are uniformly distributed circumferentially around the projection of the center line of the crankshaft (1).
Optionally, the number of the crank throws (13) and the pistons (2) is singular.
Optionally, the singular bellcrank (13) has the following arrangement order in the axial direction of the crankshaft (1): the projections of crank pins corresponding to each crank throw (13) which are sequentially arranged in the axial direction on a plane perpendicular to the central line of the crankshaft (1) are sequentially and uniformly distributed along one rotation direction of the circumference; correspondingly, the included angles between any two adjacent projections of the piston (2) perpendicular to the central line of the crankshaft (1) are equal.
Optionally, the number of the crank throws (13) and the number of the pistons (2) are 3, 5, 7, 9 and 11 respectively.
Optionally, when the number of the bellcrank (13) and the number of the pistons (2) are 3, the phase angles of the 3 bellcrank (13) are 0 °, 240 °, 480 °, and the phase angles of the 3 pistons (2) connected with the corresponding bellcrank are 0 °, 120 °, 240 °;
optionally, when the number of the bellcrank (13) and the number of the pistons (2) are both 5, the phase angles of the 5 bellcrank (13) are 0 °, 144 °, 288 °, 432 °, 576 °, and the phase angles of the 5 pistons (2) connected thereto are 0 °, 72 °, 144 °, 216 °, 288 °;
optionally, when the number of the bellcrank (13) and the number of the pistons (2) are both 7, the phase angles of 7 bellcrank (13) are 0 °, 102.857 °, 205.714 °, 308.571 °, 411.429 °, 514.286 °, 617.143 °, and the phase angles of 7 pistons (2) connected thereto are 0 °, 51.429 °, 102.857 °, 154.286 °, 205.714 °, 257.143 °, 308.571 °;
optionally, when the number of the bellcrank (13) and the number of the pistons (2) are both 9, the phase angles of the 9 bellcrank (13) are 0 °, 80 °, 160 °, 240 °, 320 °, 400 °, 480 °, 560 °, 640 °, and the phase angles of the 9 pistons (2) connected thereto are 0 °, 40 °, 80 °, 120 °, 160 °, 200 °, 240 °, 280 °, 320 °;
Optionally, when the number of the bellcrank (13) and the number of the pistons (2) are 11, the phase angles of the 11 bellcrank (13) are 0 °, 65.455 °, 130.909 °, 196.364 °, 261.818 °, 327.273 °, 392.727 °, 458.182 °, 523.636 °, 589.091 °, 654.545 °, and the phase angles of the corresponding 11 pistons (2) connected thereto are 0 °, 32.727 °, 65.455 °, 98.182 °, 130.909 °, 163.636 °, 196.364 °, 229.091 °, 261.818 °, 294.545 °, 327.273 °;
optionally, the number of the crank throws (13) and the number of the pistons (2) are two.
Optionally, the number of the crank throws (13) and the pistons (2) is 6.
Optionally, when the number of the bellcrank (13) and the number of the pistons (2) are both 6, the phase angles of the 6 bellcrank (13) are 0 °, 180 °, 240 °, 420 °, 480 °, 660 °, and the phase angles of the 6 pistons (2) connected thereto are 0 °, 90 °, 120 °, 210 °, 240 °, 330 °.
Optionally, the crankshaft (1) may comprise, in addition to the first end crank journal (11), the second end crank journal (12), a single or a plurality of intermediate crank journals, which are located between two of the bellcrank (13) of the crankshaft (1); correspondingly, an intermediate crank journal eccentric circle is arranged, an intermediate crank journal eccentric hole with the eccentric distance of e is formed in the intermediate crank journal eccentric circle, the single or a plurality of intermediate crank journals penetrate through the intermediate crank journal eccentric hole on the intermediate crank journal eccentric circle, and the intermediate crank journal eccentric circle and the machine body are rotatably mounted together.
Optionally, the eccentric circle of the middle crank journal is of a split structure, and the eccentric holes of the middle crank journal are formed by butt joint of arc holes respectively positioned at the split parts.
Optionally, a portion of the synchronizing shaft (35) extending out of the machine body serves as a power input shaft, and a mechanical structure serving as the power input shaft is provided on the extending portion.
Optionally, a portion of the synchronizing shaft (35) extending out of the body, adjacent to the gear (38), serves as a power input shaft.
Optionally, a portion of the main shaft (36) protruding out of the machine body serves as a power input shaft, and a mechanical structure serving as the power input shaft is provided on the protruding portion.
Optionally, the crank arm of the crankshaft includes a weight structure thereon.
The present embodiment also provides a water pump using the reciprocation-rotation motion converting mechanism described above.
While the invention has been described in terms of preferred embodiments, it is not intended to be limiting, but rather, it will be apparent to those skilled in the art that various changes and modifications can be made herein without departing from the spirit and scope of the invention as defined by the appended claims.
Claims (10)
1. The reciprocating-rotary motion conversion mechanism comprises a crankshaft (1), at least three pistons (2) and a machine body, and is characterized by further comprising a crankshaft planetary motion driving mechanism (3);
The crankshaft (1) comprises at least two crank journals: a first end crank journal (11), a second end crank journal (12) and at least three bellcrank (13), the first end crank journal (11) and the second end crank journal (12) being located at both ends of the crankshaft (1), respectively;
the at least three pistons (2) are rotatably connected with the at least three bellcrank by connecting rods;
the crankshaft planetary motion driving mechanism (3) with the gear structure adopts a five-shaft structure and is used for ensuring the planetary motion of the crankshaft (1) and the rotation of the crankshaft (1), and the planetary motion of the crankshaft (1) and the rotation of the crankshaft (1) are combined to enable the piston (2) to do reciprocating linear motion;
the crankshaft planetary motion driving mechanism (3) with the gear structure comprises a first external gear (31), a second external gear (31 '), a third external gear (32), a fourth external gear (32'), a seventh external gear (38), an eighth external gear (38 '), a fifth external gear (33), an annular gear (33'), a sixth external gear (34), a synchronous shaft (35), a main shaft (36) and a reversing shaft (37);
the synchronous shaft (35) is a first shaft of the five-shaft structure, the synchronous shaft (35) is arranged on a machine body through a bearing, and the first external gear (31), the third external gear (32) and the seventh external gear (38) are arranged on the synchronous shaft (35); the third external gear (32) and the seventh external gear (38) have the same number of teeth and modulus;
The first external gear (31) is meshed with the second external gear (31') through a sixth external gear (34); a reversing shaft (37) for mounting the sixth external gear (34) is a third shaft of the five-shaft structure; the second external gear (31') is arranged on a main shaft (36), and the main shaft (36) is a fourth shaft of the five-shaft structure;
the fourth external gear (32 ') and the eighth external gear (38') have the same specifications; the fourth external gear (32 ') is seated on the machine body through a first gear eccentric circle (6) which is coaxial and fixedly connected with the fourth external gear, and the eighth external gear (38 ') is seated on the machine body through a second gear eccentric circle (6 ') which is coaxial and fixedly connected with the eighth external gear; the first gear eccentric circle (6) and the second gear eccentric circle (6') are coaxial, the shaft is a second shaft of a five-shaft system, and the second shaft is coaxial with the fourth shaft; the fourth external gear (32 ') meshes with the third external gear (32), and the seventh external gear (38) meshes with the eighth external gear (38'); the eccentric holes of the first gear eccentric circle (6) and the second gear eccentric circle (6 ') are kept in phase, the first end crank journal (11) of the crankshaft (1) is rotatably mounted on the eccentric hole of the first gear eccentric circle (6), namely a first crankshaft connecting hole (32' 2), the second end crank journal (12) is rotatably mounted on the eccentric hole of the second gear eccentric circle (6 '), namely a second crankshaft connecting hole (38' 1), and the axes of the first end crank journal (11) and the second end crank journal (12) are fifth axes of the five-axis system;
The third external gear (32) and the fourth external gear (32 ') are meshed, and the seventh external gear (38) and the eighth external gear (38') are meshed; the fifth external gear (33) is mounted on the fourth shaft and is positioned outside the bearing; an inner gear ring (33') meshed with the fifth outer gear (33) is mounted on the fifth shaft; -the meshed fifth external gear (33) and ring gear (33') are interchangeable; after the exchange, the inner gear ring (33') is mounted on the main shaft (36), and the fifth outer gear (33) is mounted on a first end crank journal (11) of the crankshaft (1), namely a fifth shaft;
the above-mentioned indexing circle diameter of external gear and annular gear meets the following formula at the same time:
d 33 +2e＝d 33’
wherein d 31 Is the pitch circle diameter of the first external gear (31); d, d 31’ The pitch circle for the second external gear (31') is lowered straight; d, d 32 Is the pitch circle diameter of the third external gear (32); d, d 32’ A pitch circle diameter for a fourth external gear (32'); d, d 33 Is the pitch circle diameter of the fifth external gear (33); d, d 33’ Is the pitch circle diameter of the inner gear ring (33');
the machine body is used for mounting the piston (2) and the crankshaft planetary motion driving mechanism (3); the at least three pistons (2) are arranged in a reciprocating track of the machine body, the axis of the reciprocating track being perpendicular to the main shaft (36).
2. A reciprocating-rotary motion converting mechanism according to claim 1, characterized in that the piston (2) is a single-acting piston.
3. A reciprocating-rotary motion converting mechanism according to claim 2, characterized in that the number of pistons (2) is the same as the number of bellcrank throws (13) of the crankshaft (1), one of the pistons (2) being connected to one of the bellcrank throws (13).
4. A reciprocating-rotary motion converting mechanism according to claim 3, characterized in that the angle between any two of the bellcrank throws (13) of the crankshaft (1) is 2 times the angle between the two pistons (2) connected thereto.
5. The reciprocation-rotation motion conversion mechanism according to claim 4, wherein projections of the bell crank (13) of the crankshaft (1) on a plane perpendicular to a center line of the crankshaft (1) are circumferentially uniformly distributed with a projection of the center line of the crankshaft (1) as a center of circle.
6. The reciprocating-rotary motion converting mechanism according to claim 1, characterized in that the crankshaft (1) comprises, in addition to the first end crank journal (11), second end crank journal (12), a single or a plurality of intermediate crank journals, which are located between two of the crank throws (13) of the crankshaft (1); correspondingly, an intermediate crank journal eccentric circle is arranged, an intermediate crank journal eccentric hole with the eccentric distance of e is formed in the intermediate crank journal eccentric circle, the single or a plurality of intermediate crank journals penetrate through the intermediate crank journal eccentric hole on the intermediate crank journal eccentric circle, and the intermediate crank journal eccentric circle and the machine body are rotatably mounted together.
7. The reciprocating-rotary motion converting mechanism according to claim 6, wherein said middle crank journal eccentric circle is of split construction, and said middle crank journal eccentric hole is formed by butt-jointing arc-shaped holes respectively located at the split parts.
8. The reciprocation-rotation motion converting mechanism according to claim 1, wherein a portion of the synchronizing shaft (35) protruding from the body serves as a power input shaft, and a mechanical structure serving as the power input shaft is provided on the protruding portion.
9. The reciprocation-rotation motion converting mechanism according to claim 1, wherein a portion of the main shaft (36) protruding from the machine body serves as a power input shaft, and a mechanical structure serving as the power input shaft is provided on the protruding portion.
10. A water pump, characterized in that a reciprocating-rotary motion converting mechanism according to any one of claims 1 to 9 is used.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710826426.6A CN107725712B (en) | 2017-09-14 | 2017-09-14 | Reciprocating-rotary motion conversion mechanism and water pump thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710826426.6A CN107725712B (en) | 2017-09-14 | 2017-09-14 | Reciprocating-rotary motion conversion mechanism and water pump thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107725712A CN107725712A (en) | 2018-02-23 |
| CN107725712B true CN107725712B (en) | 2023-12-08 |
Family
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| CN108006186B (en) * | 2017-11-08 | 2020-12-01 | 襄阳涌盛星水泵有限公司 | Reciprocating-rotating motion conversion mechanism and water pump |
| IT201800004523A1 (en) * | 2018-04-16 | 2019-10-16 | Connecting rod and crank system | |
| CN110185609B (en) * | 2019-06-18 | 2024-04-16 | 江苏德华泵业有限公司 | High-pressure gear sewage pump |
| CN111457067A (en) * | 2020-05-18 | 2020-07-28 | 宁波天生密封件有限公司 | Cam coaxial sine movement mechanism and equipment adopting same |
| CN114396468B (en) * | 2021-12-30 | 2023-08-22 | 夏志辉 | Variable force transmission mechanism |
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