A transmission mechanism having multiple reverse gears

Abstract

The application provides a transmission mechanism with multiple reverse gears, which comprises an input shaft, an output shaft, a planetary gear set P2, a planetary gear set P3 and a planetary gear set P4, the planetary gear set P2 comprises a sun gear K2, a ring gear Q2, an annular carrier H2 and a planetary gear G2, the planetary gear set P4 comprises a sun gear K4, a ring gear Q4, an annular carrier H4 and a planetary gear G4, the planetary gear set P3 comprises a sun gear K3, a ring gear Q3, an annular carrier H3, a first planetary gear G3 and a second planetary gear G3, the first planetary gear G3 and the second planetary gear G3 are meshed with each other, the input shaft is connected with the sun gear K4 and the sun gear K3 in series, the output shaft is connected with the sun gear K2, and the annular carrier H2, the annular carrier H3 and the annular carrier H4 are connected in series. According to the technical scheme of the application, the first planetary gear G3 and the second planetary gear G3 rotate towards each other, the speed level difference between adjacent gears is reduced, the gear shifting between adjacent reverse gears is smoother, the three annular carriers are integrated, the overall volume of the transmission mechanism is greatly reduced, and the structure of the transmission mechanism is more compact.

Description

Technical Field

[0001] This invention belongs to the field of transmission technology, and in particular to a transmission mechanism with multiple reverse gears. Background Technology

[0002] Currently, transmission mechanisms are widely used in various vehicles and machine tools. They are important components in these mechanical devices. With the development of technology, the number of gears in existing transmission mechanisms is increasing. However, with the continuous increase in the number of gears, the number of internal parts of the transmission mechanism will inevitably increase, making the structure of the transmission mechanism increasingly complex, larger in size, and heavier in weight. Meanwhile, people have higher and higher requirements for the operational flexibility of construction machinery such as forklifts, cranes, and bulldozers, and correspondingly, the requirements for the number of gears are also increasing.

[0003] In the prior art, the disclosed document is titled: "A transmission mechanism with multiple reverse gears and a decreasing distance, comprising an input shaft, a front output shaft, a rear output shaft, an intermediate shaft, planetary gear sets P1, P2, P3, and P4. The sun gears of planetary gear sets P1, P2, and P3 are connected in parallel and then connected to the input shaft. The planet carrier of planetary gear set P1 is connected to the ring gear of planetary gear set P2 via splines. The planet carrier of planetary gear set P2, the sun gear of planetary gear set P4, and the ring gear of planetary gear set P3 are each connected via splines. The planet carrier of planetary gear set P3 is also connected in parallel with the ring gear of planetary gear set P4 and then connected to the intermediate shaft." The intermediate shaft has multiple gears connected in series at one end, with the front and rear output shafts respectively connected to the last gear. The technical solution provided in this patent document allows the transmission mechanism to have multiple reverse gears and utilizes an internal gear transmission structure as much as possible, thus reducing the overall size of the transmission mechanism to some extent. However, for some special vehicles performing special tasks, multiple reverse gears are often required to make the vehicle more maneuverable. At the same time, the overall size of the transmission mechanism should be minimized to allow for more flexible switching between reverse gears. Summary of the Invention

[0004] To solve the above-mentioned technical problems, the present invention provides a transmission mechanism with multiple reverse gears.

[0005] The present invention is achieved through the following technical solutions.

[0006] This invention provides a transmission mechanism with multiple reverse gears, including an input shaft, an output shaft, planetary gear sets P2, P3, and P4. Planetary gear set P2 includes a sun gear K2, a ring gear Q2, and a planet carrier H2. Planetary gears G2 are mounted on the planet carrier H2 and mesh between the sun gear K2 and the ring gear Q2. Planetary gear set P4 includes a sun gear K4, a ring gear Q4, and a planet carrier H4. Planetary gears G4 are mounted on the planet carrier H4 and mesh between the sun gear K4 and the ring gear Q4. Planetary gear set P3 includes a sun gear K3, a ring gear Q3, and a planet carrier H3. A first planetary gear G3 and a second planetary gear G3 are mounted on the planet carrier H3, and the first and second planetary gears G3 mesh with each other. The input shaft connects the sun gears K4 and K3 in series, the output shaft is connected to the sun gear K2, and the planet carriers H2, H3, and H4 are connected in series sequentially.

[0007] The transmission mechanism with multiple reverse gears also includes a planetary gear set P1, which includes a sun gear K1, a ring gear Q1, and a planet carrier H1. Planet gears G1 are mounted on the planet carrier H1 and mesh between the sun gear K1 and the ring gear Q1. The planet carrier H1 is also connected to the ring gear Q2, and the sun gear K1 is also connected to the output shaft.

[0008] The transmission mechanism with multiple reverse gears also includes a clutch C1, which is connected to the planetary carrier H1.

[0009] The transmission mechanism with multiple reverse gears also includes a clutch C2, which is connected to the gear ring Q1.

[0010] The sun gear K1 has 40 teeth, the planet gear G1 has 17 teeth, and the gear ring Q1 has 74 teeth.

[0011] The transmission mechanism with multiple reverse gears also includes a clutch C3, which is connected to the gear ring Q2.

[0012] The transmission mechanism with multiple reverse gears also includes a clutch F, which is connected to the gear ring Q4.

[0013] The transmission mechanism with multiple reverse gears also includes a clutch R, which is connected to the gear ring Q3.

[0014] The sun gear K2 and sun gear K4 have the same number of teeth, the gear rings Q2, Q3, and Q4 have the same number of teeth, the planet gears G2, the first planet gear G3, the second planet gear G3, and the planet gear G4 have the same number of teeth, and the ratio of the number of teeth of the sun gear K2 to the number of teeth of the sun gear K3 is 8:7.

[0015] The sun gears K2 and K4 have 40 teeth each, the gear rings Q2, Q3, and Q4 have 98 teeth each, the planet gears G2, G3 (first planet), G3 (second planet), and G4 (planetary) have 29 teeth each, and the sun gear K3 has 35 teeth.

[0016] The beneficial effects of this invention are as follows: Using the technical solution of this invention, when the clutch F brakes the ring gear Q4, it is in forward gear. At this time, the ring gear Q4 is fixed, and power is input from the sun gear K4. After being reduced in speed by the planet carrier H4, it is transmitted to the planet carrier H2. The planet carrier H2 then transmits the power to the output shaft, generating a same-direction acceleration effect. Because the first planet gear G3 and the second planet gear G3 in the planet carrier H3 mesh with each other, the first planet gear G3 and the second planet gear G3 rotate in opposite directions, thereby reducing the speed difference between adjacent gears and making the shifting between adjacent forward gears smoother. When the clutch R brakes the ring gear Q3, it is in reverse gear. At this time, the ring gear Q3 is fixed, and power is input from the sun gear K3. After being reduced in speed by the planet carrier H3, it is transmitted to the planet carrier H2. The power carrier H2 then transmits power to the output shaft, generating a reverse deceleration effect. Because the first planetary gear G3 and the second planetary gear G3 in the planetary carrier H3 mesh with each other, the first planetary gear G3 and the second planetary gear G3 rotate in opposite directions, thereby reducing the speed ratio difference between adjacent gears and making the shifting between adjacent reverse gears smoother. Compared with the prior art, the present invention, by setting the first planetary gear G3 and the second planetary gear G3 to mesh with each other in the planetary carrier H3, on the one hand, reduces the speed ratio difference between adjacent forward gears or adjacent reverse gears and improves the shifting smoothness. On the other hand, it connects the planetary carriers H4 and H2 in series through the planetary carrier H3, so that the three planetary carriers can be integrated into one unit, which greatly reduces the overall volume of the transmission mechanism and makes the structure of the transmission mechanism more compact. Attached Figure Description

[0017] Figure 1 This is a schematic diagram of the structure of the present invention;

[0018] Figure 2 This is a simplified diagram of the equivalent transmission when the present invention is in forward gear one;

[0019] Figure 3 This is a simplified diagram of the equivalent transmission when the present invention is in forward gear two;

[0020] Figure 4 This is a simplified equivalent transmission diagram of the present invention when it is in forward gear three;

[0021] Figure 5 This is a simplified diagram of the equivalent transmission when the present invention is in reverse gear one;

[0022] Figure 6 This is a simplified diagram of the equivalent transmission when the present invention is in reverse gear two;

[0023] Figure 7 This is a simplified equivalent transmission diagram of the present invention when it is in reverse gear three;

[0024] Figure 8 This is the front view of planetary array P3 of the present invention.

[0025] In the diagram: 1-Input shaft, 2-Output shaft, 3-Sun gear K3, 4-Ring gear Q3, 5-First planetary gear G3, 6-Second planetary gear G3. Detailed Implementation

[0026] The technical solution of the present invention is further described below, but the scope of protection is not limited to what is described.

[0027] like Figures 1 to 8 As shown, this invention provides a transmission mechanism with multiple reverse gears, including an input shaft, an output shaft, a planetary gear set P2, a planetary gear set P3, and a planetary gear set P4. The planetary gear set P2 includes a sun gear K2, a ring gear Q2, and a planet carrier H2. Planetary gears G2 are mounted on the planet carrier H2, meshing between the sun gear K2 and the ring gear Q2. The ratio of the number of planetary gears G2 to the number of planet carriers H2 is 3:1. The planetary gear set P4 includes a sun gear K4, a ring gear Q4, and a planet carrier H4. Planetary gears G4 are mounted on the planet carrier H4, meshing between the sun gear K4 and the ring gear Q4. The ratio of the number of gears G4 to the number of planet carriers H4 is 3:1; the planetary gear set P3 includes a sun gear K3, a ring gear Q3, and a planet carrier H3. The planet carrier H3 is equipped with a first planet gear G3 and a second planet gear G3, and the first planet gear G3 and the second planet gear G3 mesh with each other; the ratio of the number of the first planet gear G3 to the number of planet carriers H3 is 3:1, and the ratio of the number of the second planet gear G3 to the number of planet carriers H3 is 3:1; the input shaft connects the sun gears K4 and K3 in series, the output shaft is connected to the sun gear K2, and the planet carriers H2, H3, and H4 are connected in series in sequence.

[0028] Using the technical solution of this invention, when the clutch F brakes the ring gear Q4, it is in forward gear. At this time, the ring gear Q4 is fixed, and power is input from the sun gear K4. After being reduced in speed by the planet carrier H4, it is transmitted to the planet carrier H2, which then transmits the power to the output shaft, producing a same-direction speed-increasing effect. Since the first planet gear G3 and the second planet gear G3 in the planet carrier H3 mesh with each other, the first planet gear G3 and the second planet gear G3 rotate in opposite directions, thereby reducing the speed difference between adjacent gears and making the shifting between adjacent forward gears smoother. When the clutch R brakes the ring gear Q3, it is in reverse gear. At this time, the ring gear Q3 is fixed, and power is input from the sun gear K3. After being reduced in speed by the planet carrier H3, it is transmitted to the planet carrier H2, which then transmits the power to the output shaft, producing a same-direction speed-increasing effect. The force is transmitted to the output shaft, generating a reverse deceleration effect. Because the first planetary gear G3 and the second planetary gear G3 in the planetary carrier H3 mesh with each other, the first planetary gear G3 and the second planetary gear G3 rotate in opposite directions, thereby reducing the speed ratio difference between adjacent gears and making the shifting between adjacent reverse gears smoother. Compared with the prior art, the present invention, by setting the first planetary gear G3 and the second planetary gear G3 to mesh with each other in the planetary carrier H3, on the one hand, reduces the speed ratio difference between adjacent forward gears or adjacent reverse gears and improves the shifting smoothness. On the other hand, it connects the planetary carriers H4 and H2 in series through the planetary carrier H3, so that the three planetary carriers can be integrated into one unit, which greatly reduces the overall volume of the transmission mechanism and makes the structure of the transmission mechanism more compact.

[0029] Specifically, the transmission mechanism with multiple reverse gears further includes a planetary gear set P1, which includes a sun gear K1, a ring gear Q1, and a planet carrier H1. Planet gears G1 are mounted on the planet carrier H1 and mesh between the sun gear K1 and the ring gear Q1. The planet carrier H1 is also connected to the ring gear Q2, and the sun gear K1 is also connected to the output shaft. The ratio of the number of planet gears G1 to the number of planet carriers H1 is 3:1. Further, the transmission mechanism with multiple reverse gears also includes a clutch C1, which is connected to the planet carrier H1. The transmission mechanism with multiple reverse gears also includes a clutch C2, which is connected to the ring gear Q1. The sun gear K1 has 40 teeth, the planet gear G1 has 17 teeth, and the ring gear Q1 has 74 teeth.

[0030] In addition, the transmission mechanism with multiple reverse gears also includes a clutch C3, which is connected to the gear ring Q2. The transmission mechanism with multiple reverse gears also includes a clutch F, which is connected to the gear ring Q4. The transmission mechanism with multiple reverse gears also includes a clutch R, which is connected to the gear ring Q3. The sun gear K2 and sun gear K4 have the same number of teeth; the gear rings Q2, Q3, and Q4 have the same number of teeth; the planet gears G2, the first planet gear G3, the second planet gear G3, and G4 have the same number of teeth; and the tooth ratio of the sun gear K2 to the sun gear K3 is 8:7.

[0031] Preferably, the number of teeth of the sun gear K2 and sun gear K4 is 40, the number of teeth of the gear ring Q2, gear ring Q3, and gear ring Q4 is 98, the number of teeth of the planet gear G2, first planet gear G3, second planet gear G3, and planet gear G4 is 29, and the number of teeth of the sun gear K3 is 35. In this case, the working conditions and transmission ratio values ​​of each gear during shifting are shown in Table 1.

[0032] Table 1 shows the operating conditions and transmission ratios of each gear during gear shifting in this invention.

[0033]

[0034] As can be seen from Table 1, the adjacent gear ratio differences between forward gear 1, forward gear 2 and forward gear 3 are 1.59 and 0.86, respectively, while the adjacent gear ratio differences between reverse gear 1, reverse gear 2 and reverse gear 3 are 0.83 and 0.448, respectively. The gear ratio difference range is extremely small, and the transmission mechanism has good shifting smoothness. In addition, since planetary carrier H2 is connected in series with planetary carrier H3, the three planetary carriers can be integrated into one unit, which greatly reduces the overall volume of the transmission mechanism and makes the structure of the transmission mechanism more compact.

Claims

1. A transmission mechanism with multiple reverse gears, comprising an input shaft, an output shaft, a planetary gear set P2, a planetary gear set P3, and a planetary gear set P4. The planetary gear set P2 includes a sun gear K2, a ring gear Q2, and a planet carrier H2. Planetary gears G2 are mounted on the planet carrier H2 and mesh between the sun gear K2 and the ring gear Q2. The planetary gear set P4 includes a sun gear K4, a ring gear Q4, and a planet carrier H4. Planetary gears G4 are mounted on the planet carrier H4 and mesh between the sun gear K4 and the ring gear Q4. The planetary gear set P3 includes a sun gear K3, a ring gear Q3, and a planet carrier H3. A first planetary gear G3 and a second planetary gear G3 are mounted on the planet carrier H3, and the first planetary gear G3 and the second planetary gear G3 mesh with each other. The input shaft connects the sun gears K4 and K3 in series, the output shaft is connected to the sun gear K2, and the planet carriers H2, H3, and H4 are connected in series. The transmission mechanism with multiple reverse gears also includes a planetary gear set P1, which includes a sun gear K1, a ring gear Q1, and a planet carrier H1. A planet gear G1 is mounted on the planet carrier H1 and meshes between the sun gear K1 and the ring gear Q1. The planet carrier H1 is also connected to the ring gear Q2, and the sun gear K1 is also connected to the output shaft. The transmission mechanism with multiple reverse gears also includes a clutch C1, which is connected to the planetary carrier H1. The transmission mechanism with multiple reverse gears also includes a clutch C2, which is connected to the gear ring Q1; The transmission mechanism with multiple reverse gears also includes a clutch C3, which is connected to the gear ring Q2; The transmission mechanism with multiple reverse gears also includes a clutch F, which is connected to the gear ring Q4. The transmission mechanism with multiple reverse gears also includes a clutch R, which is connected to the gear ring Q3.

2. The transmission mechanism with multiple reverse gears as described in claim 1, characterized in that: The sun gear K1 has 40 teeth, the planet gear G1 has 17 teeth, and the gear ring Q1 has 74 teeth.

3. The transmission mechanism with multiple reverse gears as described in claim 1, characterized in that: The sun gear K2 and sun gear K4 have the same number of teeth, the gear rings Q2, Q3, and Q4 have the same number of teeth, the planet gears G2, the first planet gear G3, the second planet gear G3, and the planet gear G4 have the same number of teeth, and the ratio of the number of teeth of the sun gear K2 to the number of teeth of the sun gear K3 is 8:

7.

4. The transmission mechanism with multiple reverse gears as described in claim 3, characterized in that: The sun gears K2 and K4 have 40 teeth each, the gear rings Q2, Q3, and Q4 have 98 teeth each, the planet gears G2, G3 (first planet), G3 (second planet), and G4 (planetary) have 29 teeth each, and the sun gear K3 has 35 teeth.

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