WO2007143878A1

WO2007143878A1 - Transmission device of reciprocating linear type

Info

Publication number: WO2007143878A1
Application number: PCT/CN2006/001264
Authority: WO
Inventors: Bingxiao Zhu
Original assignee: Bingxiao Zhu
Priority date: 2006-06-09
Filing date: 2006-06-09
Publication date: 2007-12-21

Abstract

A transmission device of reciprocating linear type includes a premier special shaped gear (1) and a second special shaped gear (2) which can rotated in same direction of gear (1). A premier transmission teeth 4 and a rebound surface (5) are installed on a partial of the peripheral of the gear (1). A second transmission teeth (6) and a rebound surface (7) are installed on the lateral of the gear (2). This device also has a reciprocating moving rod (3) which places in between the gear (1) and gear (2), the rod (3) has a lower blocking tooth (9), a upper block tooth (10), some transmission teeth (11) for engaging with the teeth of the premier special shaped gear (1), and some transmission teeth (12) for engaging with the teeth of the second special shaped gear (2), so the rod (3) can implement a reciprocating linear movement between the gear (1) and gear (2). This device can improve efficiency of the transmission device.

Description

Linear reciprocating transmission

Technical field

The invention relates to the field of machinery, and in particular to a linear reciprocating transmission. Background of the invention

In transmissions such as engines and compressors, the crankshaft linkage structure has been widely used.

Although widely used, the crankshaft flail structure has the following disadvantages:

1. The torque generated by the crankshaft connecting rod structure is usually small, which results in a lower working efficiency of the crankshaft connecting rod structure;

2. In order to ensure the normal movement of the piston in the crankshaft connecting rod structure, the piston skirt is usually large in volume and large in mass, and the crankshaft connecting rod structure loses a large amount of energy in order to overcome the inertia generated thereby, which also leads to the crankshaft connection. The rod structure works less efficiently;

3. The manufacturing process of parts in the crankshaft connecting rod structure is complicated. Summary of the invention

In view of this, it is a primary object of the present invention to provide a linear reciprocating transmission to improve the operating efficiency of the transmission.

In order to achieve the above object, the technical solution of the present invention is achieved as follows:

The invention discloses a linear reciprocating transmission device, which comprises a first profile wheel 1 and a second profile wheel 2 which are rotatable in the same direction. The first profile wheel 1 is provided with a first profile wheel side transmission tooth 4 and a first a special-shaped wheel side rebounding surface 5, the second profiled wheel 2 is provided with a second profiled wheel side transmission tooth 6 and a second profiled wheel side rebounding surface 7; the device further comprises a first profiled wheel 1 a reciprocating rod 3 between the second profiled wheels 2, the reciprocating rod 3 is provided with a lower stop bounce tooth 9, an upper stop bounce tooth 10, a first profile wheel side pin gear 11 and a second profile wheel side gear gear 12;

Wherein, in the case where the second profile wheel side transmission tooth 6 and the second profile wheel side lever gear tooth 12 are engaged, the first profile wheel side rebound surface 5 and the upper stop rebound tooth 10 are formed to prevent the reciprocating rod 3 from continuing. a sliding contact relationship, and the first profile wheel side transmission tooth 4 and the first profile wheel side shaft gear tooth 11 form an engagement relationship for the reverse rotation of the reciprocating rod 3;

In the case where the first profile wheel side transmission tooth 4 and the first profile wheel side lever gear tooth 11 are engaged, the formation of the reciprocating lever 3 is prevented from continuing to slide between the second profile wheel side rebound face 7 and the lower stop rebound tooth 9. In the relationship, the second profile wheel side gear 6 and the second profile wheel side gear tooth 12 form an engaging relationship for the reverse rotation of the reciprocating rod 3.

The reciprocating rod 3 is provided with a guiding structure that supports its own linear reciprocating sliding.

The guiding structure is a groove or a convex rail.

The reciprocating rod 3 is a double-sided rack having a I-shaped structure.

One or both ends of the reciprocating rod 3 are further connected to the piston.

The number of M of the first profile wheel 1 and the second profile wheel 2 is 3, and the number of teeth is 8 respectively; the number of M of the first profile wheel side gear tooth 11 and the second profile wheel side gear tooth 12 is 3, and the number of teeth is respectively It is 8.

The first profile wheel 1 is further connected to the first transmission wheel 13 via the first transmission shaft 16, and the second profile wheel 2 is further connected to the second transmission wheel 14 via the second transmission shaft 17; the first transmission wheel 13 and the second transmission wheel 14 is for supporting the first shaped wheel 1 and the second shaped wheel 2 to rotate in the same direction.

The first transmission wheel 13 and the second transmission wheel 14 are gears that are commonly fitted in the transmission belt 15; or, the first transmission wheel 13 and the second transmission wheel 14 are gears that mesh with a gear between each other.

The first transmission shaft 16 or the second transmission shaft 17 is further connected with a power output device. The tooth heights of the teeth on the first profiled wheel 1 and the second profiled wheel 2 are respectively: the maximum distance from the inner circle of the profiled wheel to the center of the profile wheel.

Compared with the prior art, the linear reciprocating transmission provided by the present invention allows the forces of the first and second irregularities 1 and 2 to be directly transmitted to the reciprocating rod 3, thereby achieving high work efficiency. Moreover, the reciprocating rod 3 that performs the linear reciprocating motion is in the same direction as the piston connected thereto, so that the piston no longer needs a large skirt, thereby greatly reducing the piston mass, which can significantly reduce the inertia of the piston. The lost energy can significantly improve work efficiency. Furthermore, the production process of the apparatus of the present invention is very simple. In addition, if a plurality of linear reciprocating transmissions of the present invention are provided in an engine, a compressor, etc., one or more of the linear reciprocating transmissions may be turned off or on according to actual needs, to flexibly control the actual work. effectiveness. Drawing tube

1 is a schematic view showing the structure and principle of a linear reciprocating transmission device according to a preferred embodiment of the present invention;

Figure 2 is a schematic diagram for determining the number of teeth of the drive on the profile wheel. Mode for carrying out the invention

The present invention will be described in detail below with reference to the accompanying drawings and specific embodiments.

The linear reciprocating transmission device provided by the invention comprises a first profile wheel 1 and a second profile wheel 2 which are rotatable in the same direction. The first profile wheel 1 is provided with a first profile wheel side transmission tooth 4 and a first profile wheel. a side of the second outer wheel 2 is provided with a second profile wheel side transmission tooth ⁶ and a second profile wheel side rebound surface 7; the device further comprises a first profile wheel 1 and a second profile wheel 2 Reciprocating rod 3, the reciprocating rod 3 is provided with a lower stop rebounding tooth 9, an upper stop rebounding tooth 10, a first profiled wheel side shaft gear 11 and a second profile wheel side gear gear 12; Wherein, in the case where the second profile wheel side transmission tooth 6 and the second profile wheel side lever gear tooth 12 are engaged, the first profile wheel side rebound surface 5 and the upper stop rebound tooth 10 are formed to prevent the reciprocating rod 3 from continuing. a sliding contact relationship, and the first profile wheel side transmission tooth 4 and the first profile wheel side body gear tooth 11 form an engagement relationship for the reverse rotation of the reciprocating rod 3;

In the case where the first profile wheel side transmission tooth 4 and the first profile wheel side lever gear tooth 11 are engaged, the formation of the reciprocating lever 3 is prevented from continuing to slide between the second profile wheel side rebound face 7 and the lower stop rebound tooth 9. In the relationship, the second profile wheel side gear 6 and the second wheel side gear gear 12 form an engaging relationship for the reverse rotation of the reciprocating rod 3.

Referring to Figure 1, Figure 1 is a schematic view showing the structure and principle of a linear reciprocating transmission according to a preferred embodiment of the present invention. In Fig. 1, the first profile wheel 1 and the second profile wheel 2 can only rotate in the same direction, and the steering is clockwise; and, the first profile wheel 1 and the second profile wheel 2 are respectively provided with a first profile wheel side transmission. The tooth 4, the first profile wheel side rebound face 5 and the second profile wheel side drive tooth 6, and the second profile wheel side rebound face 7. A reciprocating rod 3 is further disposed between the first profiled wheel 1 and the second profiled wheel 2, and the reciprocating rod 3 is provided with a groove 8, a lower stop bounce tooth 9, an upper stop bounce tooth 10, and a first profile wheel The side rod body drive teeth 11 and the second profile wheel side rod body drive teeth 12.

Specifically, the groove 8 on the reciprocating rod 3 coincides with the convex rail provided on the inner wall of the apparatus such as the engine, the compressor, etc., so that the reciprocating rod 3 can be grooved along the groove 8 inside the engine, the compressor, or the like. Sliding; of course, the groove 8 can also be designed as a convex rail, and the convex rail can be matched with the groove provided on the inner wall of the engine, the compressor, etc., to ensure that the reciprocating rod 3 can be convex along itself. The groove of the rail slides inside the device such as an engine or a compressor.

When the first profile wheel 1 rotates clockwise, and the first profile wheel side drive tooth 4 thereon is just engaged with the first profile wheel side gear gear 11 on the reciprocating bar 3, the second on the second profile wheel 2 There is no meshing relationship between the profiled wheel side drive teeth 6 and the second profile wheel side body drive teeth 12 on the shuttle bar 3. Obviously, the clockwise rotation of the first profiled wheel 1 and its meshing relationship with the reciprocating rod 3 will cause the reciprocating rod 3 to slide downward. As the first profile wheel 1 rotates clockwise, the first profile wheel 1 will eventually lose its meshing relationship with the reciprocating rod 3; at this time, the second profile wheel side rebound surface 7 on the second profile wheel 2 will be due to the second profile. The clockwise rotation of the wheel 2 interferes with the lower stop rebounding teeth 9 on the reciprocating rod 3. As the second profile wheel 2 continues to rotate clockwise, the lower stop bounce tooth 9 pushes the reciprocating bar 3 upward and further drives the second profile wheel side drive tooth 6 and the second profile wheel side bar on the reciprocating bar 3 The teeth 12 mesh. In this case, as the second profile wheel 2 rotates clockwise, the second profile wheel 2 will eventually lose its meshing relationship with the reciprocating rod 3.

When the second profile wheel 2 loses the meshing relationship with the reciprocating rod 3, the first profile wheel side rebound surface 5 on the first profile wheel 1 will be stopped by the clockwise rotation of the first profile wheel 1 and the reciprocating rod 3 The position rebounding teeth 10 are in conflict. As the first profile wheel 1 continues to rotate clockwise, the upper stop bounce tooth 10 pushes the reciprocating bar 3 downward, and further causes the first profile wheel side drive tooth 4 and the first profile wheel side bar on the reciprocating bar 3 The drive teeth 11 mesh. In this case, as the first profile wheel 1 rotates clockwise, the first profile wheel 1 will eventually lose its meshing relationship with the reciprocating rod 3.

It can be seen that with the clockwise rotation of the first profile wheel 1 and the second profile wheel 2, the reciprocating bar 3 can slide back and forth along the groove of the groove 8 inside the engine, the compressor or the like.

Of course, in practical applications, the first profile wheel 1 and the second profile wheel 2 can also be rotated counterclockwise. In this case, it is only necessary to horizontally flip the first profile wheel 1, the second profile wheel 2, and the striker 3 horizontally. When the first profile wheel 1 and the second profile wheel 2 are rotated counterclockwise, the principle of the reciprocating rod 3 reciprocating up and down along the groove of the groove 8 is the same as that shown in Fig. 1.

It can be seen that, with the counterclockwise rotation of the first profile wheel 1 and the second profile wheel 2, the reciprocating bar 3 can also slide back and forth along the groove of the groove 8 inside the engine, the compressor or the like.

Whether the clockwise rotation or the counterclockwise rotation, when the first profile wheel 1 is engaged with the reciprocating rod 3, there is inevitably no meshing relationship between the second profile wheel 2 and the reciprocating rod 3, namely: the first profile When the wheel 1 is engaged with the reciprocating rod 3, the second profiled wheel 2 is idling; likewise, when the second profiled wheel 2 is engaged with the reciprocating rod 3, there is inevitably no meshing relationship between the first profiled wheel 1 and the reciprocating rod 3, namely: When the second profile wheel 2 is engaged with the reciprocating rod 3, the first profile wheel 1 is idling. In practical applications, the first profiled wheel 1 and the second profiled wheel ² are normally in a meshing state for half a week, and the half cycle is in an idling state.

In order to ensure the smooth operation of the linear reciprocating gear in Figure 1, the following points usually need to be considered:

1. The first profile wheel 1 and the second profile wheel 2 are preferably capable of synchronous rotation;

2. The number of teeth included in the first profile wheel side transmission tooth 4 and the second profile wheel side transmission tooth 6 can ensure that the first profile wheel 1 is idling when the first profile wheel 1 is engaged with the reciprocating bar 3; and the second profile wheel 2 When the reciprocating rod 3 is engaged, the first special-shaped wheel 1 is idling.

If the linear reciprocating transmission in FIG. 1 does not work smoothly during application, the first profile wheel side gear tooth 11 and/or the second profile wheel side gear tooth 12 on the reciprocating rod 3 may be adjusted, or The position of the first profile wheel 1 and/or the second profile wheel 2 is adjusted, and the position of the first profile wheel side drive tooth 4 and/or the second profile wheel side drive tooth 6 can also be adjusted.

Generally, the reciprocating rod 3 is a double-sided rack having a I-shaped structure, and one or both ends thereof may be connected to a piston in an engine, a compressor, etc.; the first profiler wheel side transmission tooth 4, the second profile wheel side transmission The tooth 6, the first profile wheel side gear tooth 11 and the second profile wheel side gear tooth 12 have the same number of teeth; the first profile wheel side rebound face 5, the upper stop rebound tooth 10, and the second variant wheel side rebound The position of the face 7 and the lower stop rebounding teeth 9 is preferably such that the reciprocating rod 3 can receive the maximum force when changing the sliding direction.

In the above, only the key components for ensuring the smooth operation of the linear reciprocating transmission in FIG. 1 are introduced; in practical applications, the first profiled wheel 1 can be further passed through the first The transmission shaft 16 is connected to the first transmission wheel 13, and the second profile wheel 2 is connected to the second transmission wheel 14 via the second transmission shaft 17. In FIG. 1, the first transmission shaft 16 and the second transmission shaft 17 are not completely drawn, which means that there is a connection relationship between the first-shaped wheel 1 and the first transmission shaft 16, and the second-shaped wheel 2 and the second transmission are indicated. There is a connection relationship between the shafts 17.

In practical application, the transmission belt 15 sleeved on the first transmission wheel 13 and the second transmission wheel 14 can ensure that the first transmission wheel 13 and the second transmission wheel 14 can rotate in the same direction; of course, the transmission belt 15 can also be omitted. Rather, a gear is engaged between the first transmission wheel 13 and the second transmission wheel 14 to enable the first transmission wheel 13 and the second transmission wheel 14 to rotate in the same direction. Obviously, the synchronous co-rotation of the first transmission wheel 13 and the second transmission wheel 14 can ensure the synchronous co-rotation of the first profile wheel 1 and the second profile wheel 2.

In a practical application, the first transmission shaft 16 can be used as a driving shaft, and one end of the first transmission shaft 16 is connected with a power output device such as a flywheel to output power; and the second transmission shaft 17 can also be used as a driving shaft, and One end of the second transmission shaft 17 is connected to a power output device such as a flywheel to output power. Of course, the reciprocating rod 3 can also be used as a device for outputting power. The first drive wheel 13 and the second drive wheel 14 are typically the same common full-toothed gear.

3 may be generally of the reciprocating rod can reach the highest position and the lowest position of the bottom dead center position are referred to, the top dead center position ₀

In order to ensure the smooth operation of the linear reciprocating transmission in Fig. 1, the first profiled wheel 1 and the second profiled wheel 2 can be designed with reference to Fig. 2.

In Fig. 2, a circle 0 is made, and the circle 0 is coincident with the outer circle of the irregular wheel; the diameter BC of the circle 0 is also made, and the line B is crossed to a point A on the circle 0. On this basis, select the appropriate M number for circle 0 so that the position of point A can satisfy the following two conditions:

1. The line where AB is located is the inner circle tangent of the shaped wheel, and the maximum distance from line AB to circle 0 is equal to the tooth height;

2. The length of the arc AC is just an integer multiple of the pitch, which makes the two points A and C different. The vertices of the two teeth on the shape wheel, and the teeth of the two points A and C and the number of teeth of the teeth contained between the two points of C are the number of teeth to be set on the profile wheel.

In addition, the distance that the reciprocating rod 3 can slide between its upper stop position and the lower stop position should be equal to the arc AC+ line segment AB, based on which the size of the reciprocating rod 3, the shaped wheel and its teeth can be easily determined. Setting parameters.

It should be noted that, in order to ensure that the first profile wheel 1 and the second profile wheel 2 can be smoothly engaged with the reciprocating rod 3 at different times, respectively, and the meshing neutral position does not occur, the first profile wheel 1 and the second profile can be appropriately reduced. The circumference of the wheel 2 is such that one of the profile wheel and the reciprocating rod 3 ends the meshing relationship, while the other profile wheel and the reciprocating rod 3 just engage.

Based on the principles in Figure 1, Figure 2, and the experience accumulated in practical applications, the devices in Figure 1 can be set to the following dimensions:

The length of the reciprocating rod 3 is 13cra, and the first-shaped wheel-side rod-shaped driving tooth 11 is lower than the second-shaped wheel-side rod-shaped driving tooth 12 by about 2/3 pitch, and the pitch is the special-shaped wheel-side shaft transmission The pitch between the teeth; the closest tooth distance of the first profile wheel side gear tooth 11 to the lower stop rebound tooth 10 is about 1.6 cm, and the second profile wheel side gear tooth 12 The tooth closest to the top stop bounce tooth 9 is about 1.6 cm from the upper stop bounce tooth 9; the M number of the first profile wheel side ^" body drive tooth 11 and the second profile wheel side pin drive tooth 12 is 3, The number of teeth is 8 respectively; the upper stop bounce tooth 9 and the lower stop bounce tooth 10 are about 1.3 cm high; the distance that the reciprocating rod 3 can slide between its upper stop and lower stop is about 11.4 cm.

Further, the first profile wheel 1 and the second profile wheel 2 have a diameter of about 7.37 cm, an M number of 3, and a number of teeth of eight.

As can be seen from the above, the linear reciprocating transmission provided by the present invention allows the forces of the first profiled wheel 1 and the second profiled wheel 2 to be directly transmitted to the reciprocating rod 3, thereby achieving high work efficiency. And, the direction of movement of the reciprocating rod 3 that reciprocates linearly and the piston connected thereto Consistent with PT/CN2006/001264, this eliminates the need for a large skirt for the piston, which greatly reduces the mass of the piston, which significantly reduces the energy lost by overcoming the inertia of the piston, thus significantly increasing work efficiency. Furthermore, the production process of the apparatus of the present invention is very simple.

In addition, if a plurality of linear reciprocating transmissions of the present invention are provided in an engine, a compressor, etc., one or more of the linear reciprocating transmissions may be turned off or turned on according to actual needs; The actual working efficiency of equipment such as compressors has become possible, effectively solving the problem of insufficient idle burning and idle consumption.

Specifically, there are various methods for closing or opening the linear reciprocating transmission, such as: ending or starting the engagement relationship with the reciprocating rod 3.

Furthermore, the linear reciprocating transmission of the present invention structurally supports other types of transmissions as far as possible in the prior art; so that when the linear reciprocating transmission is provided in an engine, a compressor, etc., only a slight change of the engine is required. , the bottom structure of the compressor and other equipment and a few components such as the piston. It is apparent that the linear reciprocating transmission of the present invention is easy to generalize.

In summary, the linear reciprocating transmission provided by the present invention can effectively improve the working efficiency of the transmission device. .

Claims

Claim

A linear reciprocating transmission, characterized in that the device comprises a first profiled wheel (1) and a second profiled wheel (2) which are rotatable in the same direction, and the first profiled wheel (1) is provided with a first The profiled wheel side transmission tooth (4) and the first profile wheel side rebound surface (5), the second profile wheel (2) is provided with a second profile wheel side transmission tooth (6) and a second profile wheel side rebound surface (7) The device further includes a reciprocating rod (3) disposed between the first profiled wheel (1) and the second profile wheel (2), and the reciprocating rod (3) is provided with a lower stop bounce tooth (9), a stop rebounding tooth (10), a first profile wheel side shaft gear (11) and a second profile wheel side gear gear (12);

Wherein, in the case where the second profile wheel side transmission tooth (6) and the second profile wheel side gear body transmission tooth (12) are finished meshing, the first profile wheel side rebound face (5) and the upper stop rebound tooth (10) An intermeshing relationship is formed between the reciprocating rod (3) to prevent the reciprocating rod (3) from continuing to slide, and the first deformed wheel side driving tooth (4) and the first deformed wheel side rod driving tooth (11) form an engagement for reversing the reciprocating rod (3). Relationship

In the case where the first profile wheel side transmission tooth (4) and the first profile wheel side shaft gear tooth (11) are finished meshing, between the second profile wheel side rebound face (7) and the lower stop rebound tooth (9) An interference relationship is formed to prevent the reciprocating rod (3) from continuing to slide, and the second profile wheel side transmission tooth (6) and the second profile wheel side shaft gear (12) form an engaging relationship for the reverse rotation of the reciprocating rod (3).

2. Apparatus according to claim 1, characterized in that the reciprocating rod (3) is provided with a guiding structure for supporting its own linear reciprocating sliding.

3. Apparatus according to claim 1 wherein said guiding structure is a groove or a raised rail.

4. Apparatus according to claim 1 or 2, characterized in that the reciprocating rod (3) is a double-sided rack with a I-shaped structure.

5. Apparatus according to claim 1 or 2, characterized in that one or both ends of the reciprocating rod (3) are further connected to the piston.

6. Apparatus according to claim 1 wherein:

The first profile wheel (1) and the second profile wheel (2) have an M number of 3 and a number of teeth of 8, respectively; the first profile wheel side body gear (11) and the second profile wheel side gear gear (12) The number of M is 3, and the number of teeth is 8.

7. Apparatus according to claim 1 or 2, characterized in that:

The first profile wheel (1) is further connected to the first transmission wheel (13) through the first transmission shaft (16), and the second profile wheel (2) is further passed through the second transmission shaft (17) and the second transmission wheel (14) Connected; the first transmission wheel (13) and the second transmission wheel (14) are used to support the first profile wheel (1) and the second profile wheel (2) to rotate in the same direction.

8. Apparatus as claimed in claim 7, characterized in that:

The first transmission wheel (13) and the second transmission wheel (14) are gears that are commonly sleeved in the transmission belt (15);

Alternatively, the first transmission wheel (13) and the second transmission wheel (14) are gears in which a gear is meshed with each other.

9. Apparatus according to claim 7 wherein:

The first transmission shaft (16) or the second transmission shaft (17) is further connected with a power output device.

10. Apparatus according to claim 1 wherein:

The tooth heights of the teeth on the first profile wheel (1) and the second profile wheel (2) are respectively: the maximum distance from the inner circle tangent of the profile wheel to the center of the profile wheel.