Bidirectional transmission

Abstract

The present invention discloses a bidirectional transmission transmission, comprising a power input gear pair, a power output gear pair and a bidirectional transmission device for transmission between the power input gear pair and the power output gear pair. The bidirectional transmission device adopts a structure in which a transmission shaft and a transmission sleeve are time-set with an engagement groove and two clutch grooves in a set phase. When one of the clutch grooves and the engagement groove is in an overlapping phase and both correspond to an engagement block, the engagement block radially extends outward and is simultaneously engaged with the clutch groove and the engagement groove. When the transmission shaft rotates in a direction exceeding the engagement groove on a circumference toward the clutch groove, the engagement block engages with the engagement groove and the transmission shaft is transmitted to the transmission sleeve (if the transmission sleeve is active, the transmission direction is opposite). When the transmission shaft rotates in the opposite direction, since the end of the clutch groove on the circumference is within the range of the engagement groove, the engagement block is driven by the transmission shaft to cross the clutch groove and is pressed back radially by the inner circle of the transmission sleeve, thereby causing the engagement block to be disengaged from the engagement groove to form overrunning.

Description

Technical Field

[0001] The invention relates to a mechanical transmission component, in particular to a bidirectional transmission speed changer. Background Art

[0002] Bidirectional transmission and the ability to overtake in the reverse direction of transmission is a transmission structure widely required in the field of mechanical transmission. It is usually achieved by switching between two reversely arranged one-way devices (overrunning clutch, ratchet transmission) or simply switching gear transmission.

[0003] That is to say, in the prior art, in the structures that require two-way transmission, most of them are formed by combining single-function unidirectional transmission structures, which need to be switched when in use, and the overall structure is relatively complex, which increases the size of the speed change mechanism, increases the cost, and also reduces the transmission efficiency. For agricultural machinery and other mechanical equipment that require two-way transmission, this two-way transmission structure is not conducive to on-site operation due to its large size, and is also costly. In addition, the load-bearing capacity of the above-mentioned traditional transmission structure is also relatively low.

[0004] Therefore, a simple two-way transmission structure is needed, which has a simple structure, a small size, and is easy to switch between two-way transmissions. The structure is suitable for occasions such as agricultural machinery that require two-way transmissions. Summary of the invention

[0005] In view of this, the present invention provides a bidirectional transmission which has a simple structure, a small size, and is easy to switch between bidirectional transmissions. The transmission is suitable for agricultural machinery and other occasions where bidirectional transmissions are required.

[0006] The bidirectional transmission of the present invention comprises a power input gear pair, a power output gear pair and a bidirectional transmission device for transmission between the power input gear pair and the power output gear pair, wherein the bidirectional transmission device comprises a transmission shaft and a transmission sleeve outermostly disposed on the transmission shaft;

[0007] The inner circle of the transmission sleeve is provided with a transmission meshing groove, a first clutch groove and a second clutch groove, wherein the first clutch groove and the second clutch groove are arranged at two axial ends of the transmission meshing groove and are both axially connected with the transmission meshing groove;

[0008] In the circumferential position:

[0009] One end of the first clutch groove exceeds the transmission meshing groove, and the other end is located within the range of the transmission meshing groove; the second clutch groove exceeds the transmission meshing groove at one end opposite to the first meshing groove in the circumferential direction, and the other end is located within the range of the transmission meshing groove;

[0010] The transmission shaft is circumferentially transmittable and radially reciprocatingly slidable and is provided with a meshing block;

[0011] The axial width of the engagement block is greater than the axial width of the transmission engagement groove, and the transmission shaft and the transmission sleeve can be driven to slide relative to each other in the axial direction so that the engagement block is in the axial position:

[0012] Located in the range of the first clutch slot and the transmission meshing slot, or located in the range of the second clutch slot and the transmission meshing slot, or located in the range of the first clutch slot, the transmission meshing slot, and the second clutch slot;

[0013] Alternatively, the axial width of the engagement block is equal to or smaller than the axial width of the transmission engagement groove. Then, when driven, the engagement block is in the axial position: in the range of the first clutch groove and the transmission engagement groove, or in the range of the second clutch groove and the transmission engagement groove, or in the range of the transmission engagement groove.

[0014] Furthermore, the groove walls at both ends of the first clutch groove and the second clutch groove in the circumferential direction are inclined outward to form a slope that smoothly transitions to the inner circle of the transmission sleeve.

[0015] Furthermore, the transmission sleeve includes a sleeve body located in the axial middle part and a first pressure plate and a second pressure plate respectively fixed at both ends of the sleeve body, the first clutch groove is arranged on the inner circle of the first pressure plate, and the second clutch groove is arranged on the inner circle of the second pressure plate.

[0016] Furthermore, an engagement block installation groove is radially provided on the transmission shaft, and the engagement block is installed in the engagement block installation groove via a spring that applies a radial outward preload force to the engagement block.

[0017] Furthermore, one of the transmission engagement grooves, the first clutch groove and the second clutch groove forms a groove group, and the groove groups are at least two evenly distributed along the circumferential direction; and the engagement blocks are at least two evenly distributed along the circumferential direction.

[0018] Furthermore, the groove groups are several groups arranged radially opposite to each other, there are two engaging blocks, the mounting groove is a radial through groove, the two engaging blocks are arranged back to back in the mounting groove and the preload force is applied to both ends of the same spring.

[0019] Further, the transmission sleeve can be driven to slide axially relative to the transmission shaft, so that the engagement block is located in the range where the first clutch groove and the transmission engagement groove are located, or, in the range where the second clutch groove and the transmission engagement groove are located, or, in the range where the first clutch groove, the transmission engagement groove and the second clutch groove are located;

[0020] The outer circle of the transmission shaft sleeve is fixed with an external gear, and the power is output through the external gear;

[0021] The outer circle of the transmission sleeve is also processed with a fork groove, and a driving fork extends into the fork groove to drive the transmission sleeve to slide axially relative to the transmission shaft.

[0022] Furthermore, the first pressure plate and the second pressure plate are respectively detachably fixedly connected to the shaft sleeve body by bolts evenly distributed in the circumferential direction.

[0023] Further, the power input gear pair comprises a power input driving gear and a power input driven gear meshing with the power input driving gear, and the power input driven gear is transmission-coordinatedly arranged on the transmission shaft;

[0024] The power output gear pair includes the outer gear as the power output driving gear and the power output driven gear meshing with the power output driving gear. The power output driven gear is transmission-coordinated with a power output shaft, and a terminal output gear is transmission-coordinated with the power output shaft. The terminal output gear outputs power to the vehicle differential.

[0025] Beneficial effects of the present invention: The bidirectional transmission of the present invention adopts a structure in which a transmission shaft and a transmission sleeve are time-arranged with meshing grooves and two clutch grooves in a set phase. When one of the clutch grooves and the meshing groove is in an overlapping phase and both correspond to the meshing block, the meshing block extends radially outward and simultaneously engages with the clutch groove and the meshing groove. When the transmission shaft rotates in a direction beyond the meshing groove on the circumference toward the clutch groove, the meshing block meshes with the meshing groove and the transmission shaft is transmitted to the transmission sleeve (if the transmission sleeve is active, the transmission direction is opposite). When the transmission shaft rotates in the opposite direction, since the end of the clutch groove on the circumference is within the range of the meshing groove, the meshing block is driven by the transmission shaft to cross the clutch groove and is transmitted The inner circle of the moving shaft sleeve is pressed back radially, so that the meshing block is disengaged from the meshing groove, forming an overrunning; similarly, the driving transmission shaft and the transmission shaft sleeve slide axially relative to each other, so that the meshing block is located within the range of the other clutch groove and the meshing groove. Since the direction in which the other clutch groove exceeds the meshing groove on the circumference is opposite, reverse transmission can be achieved; and when the meshing block is located within the range of the two clutch grooves and the meshing grooves, idling can be achieved; thus, a simple structure can be used to achieve switching between dual lateral transmission and idling. Compared with the structure of the prior art, it has a smaller volume, extremely low manufacturing cost, easier switching of bidirectional transmission, and a stronger load-bearing capacity, and is suitable for agricultural machinery and other occasions that require bidirectional transmission. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] The present invention will be further described below in conjunction with the accompanying drawings and embodiments.

[0027] Figure 1 is a longitudinal cross-sectional view of the bidirectional transmission device (reflecting the first transmission direction);

[0028] Figure 2 for Figure 1 Section view along AA direction;

[0029] Figure 3 for Figure 1 A radial cross-sectional view at the meshing groove;

[0030] Figure 4 is a longitudinal sectional view of the bidirectional transmission device (reflecting the second transmission direction);

[0031] Figure 5 Bit Figure 4 Section view along BB;

[0032] Figure 6 for Figure 4 A radial cross-sectional view at the meshing groove;

[0033] Figure 7 is a shape diagram of the first clutch groove and the second clutch groove;

[0034] Figure 8 It is a schematic diagram of the local structure of the transmission of the present invention. DETAILED DESCRIPTION

[0035] like Figure 1-8 As shown: the bidirectional transmission of this embodiment includes a power input gear pair, a power output gear pair and a bidirectional transmission device located between the power input gear pair and the power output gear pair for transmission, the bidirectional transmission device includes a transmission shaft 1 and a transmission sleeve outerly mounted on the transmission shaft 1; the transmission device is located between the power input gear pair and the power output gear pair, that is, used to transmit power between the two, and will not be described in detail here;

[0036] The inner circle of the transmission sleeve is provided with a transmission meshing groove 201, a first clutch groove 301 and a second clutch groove 401. The first clutch groove 301 and the second clutch groove 401 are arranged at the axial ends of the transmission meshing groove 201 and are axially connected with the transmission meshing groove 201. Of course, the transmission meshing groove, the first clutch groove and the second clutch groove are all radially recessed outward and have a certain length in the circumferential direction. At the same time, they are connected in the axial direction, which will not be described in detail here.

[0037] In the circumferential position:

[0038] One end of the first clutch groove 301 exceeds the transmission meshing groove 201, and the other end is located within the range of the transmission meshing groove 201, that is, the first clutch groove 301 and the transmission meshing groove 201 partially overlap in the circumferential direction (axial projection) (the overlapping portion should be able to accommodate the meshing block described below, which will not be repeated here), and the first clutch groove 301 and the transmission meshing groove 201 each exceed both ends in the circumferential direction; the second clutch groove exceeds the transmission meshing groove 201 at one end opposite to the first meshing groove in the circumferential direction, and the other end is located within the range of the transmission meshing groove 201, that is, the second clutch groove is similar to the first meshing groove in structure and shape, except that the direction in which the second clutch groove exceeds the transmission meshing groove in the circumferential direction is opposite to that of the first clutch groove;

[0039] The transmission shaft 1 is circumferentially translatable and radially reciprocatingly slidable and is provided with a meshing block;

[0040] like Figure 1 Combined with Figure 2 and Figure 3 , the axial width of the meshing block is greater than the axial width of the transmission meshing groove, and the transmission shaft 1 and the transmission sleeve can be driven to slide relative to each other in the axial direction (the transmission sleeve can be driven to slide axially, or the transmission shaft can be driven to slide axially, both of which can achieve the purpose of relative sliding) so that the meshing block is in the axial position:

[0041] It is in the range of the first clutch groove 301 and the transmission meshing groove 201. At this time, when the transmission shaft 1 drives the meshing block to rotate in the clockwise direction, that is, in the direction in which the first clutch groove exceeds the transmission meshing groove (or when the transmission sleeve is driven to rotate in the counterclockwise direction), the meshing block first approaches the groove wall of the transmission meshing groove in this direction to form transmission; when the transmission shaft drives the meshing block to rotate in the counterclockwise direction (or when the transmission sleeve is driven to rotate in the clockwise direction), since the end corresponding to the first clutch groove is located within the range of the transmission meshing groove and is inclined outward, a cam effect is formed, and radial inward pressure is applied to the meshing block. Therefore, when the meshing block passes through the end and reaches the inner circle of the transmission sleeve, it is radially compressed to disengage from the transmission meshing groove, thereby forming overrunning;

[0042] Similarly, if Figure 4 Combined with Figure 5 and Figure 6 When the meshing block 5 is in the range of the second clutch groove 401 and the transmission meshing groove 201, reverse transmission is formed, that is, the transmission shaft is the driving shaft, and it is transmitted in the counterclockwise direction, and vice versa; thus, when the transmission shaft and the transmission sleeve slide relative to each other in the axial direction and the meshing block is in the above two different positions, a bidirectional transmission structure can be completed;

[0043] Of course, when the meshing block is simultaneously in the range of the first clutch slot 301, the transmission meshing slot 201 and the second clutch slot; at this time, whether the transmission shaft rotates clockwise or counterclockwise, it is in an overrunning state, thereby forming an idling state;

[0044] Of course, to achieve the above-mentioned overtaking state, the transition between the groove wall of the first clutch groove and the second clutch groove at least at one end within the range of the meshing transmission groove in the circumferential direction and the inner circle of the transmission sleeve presents an outward slope to ensure that when the transmission shaft drives the meshing block to pass this position, it can slide smoothly to the inner circle position of the transmission sleeve to be compressed and separated from the transmission meshing groove. Of course, in order to enable the meshing block to achieve radial reciprocating sliding, it is necessary to apply a radial outward pre-tightening force to it, which will not be repeated here; and the groove walls at both ends of the circumferential direction of the transmission meshing groove should be right-angled or acute-angled transitions to ensure reliable transmission meshing with the meshing block.

[0045] Of course, because the axial width of the meshing block is in a different ratio to the axial width of the transmission meshing groove, the transmission matching effect is different; for example, if the axial width of the meshing block is equal to or smaller than the axial width of the transmission meshing groove, then when driven, the meshing block is in the axial position:

[0046] When the engagement block is in the range of the first clutch groove and the transmission meshing groove, or when the engagement block is in the range of the second clutch groove and the transmission meshing groove, the above two structural states are the same as the aforementioned forward and reverse transmission states, and forward and reverse transmission can be realized; however, when the engagement block is in the range of the transmission meshing groove, it is in a constant meshing state, and a state of both forward and reverse transmission can be realized to adapt to different transmission requirements.

[0047] In this embodiment, the groove walls at both ends of the first clutch groove 301 and the second clutch groove 401 in the circumferential direction are inclined outward to form a slope that smoothly transitions with the inner circle of the transmission shaft sleeve; the smooth transition slope can make the engagement block 5 have less resistance and noise when entering or leaving the first clutch groove 301 and the second clutch groove 401 in the circumferential direction; Figure 7 As shown, since the shapes of the first clutch groove and the second clutch groove are the same but the installation phases are different, they are represented by the same figure; the groove walls at both ends of the circumferential direction of the first clutch groove 301 and the second clutch groove 401 are both curved and smoothly transitioned, and the slope is as gentle as possible when the circumferential size allows, which reduces noise and resistance while also reducing the impact force of the meshing block.

[0048] In this embodiment, the transmission sleeve includes a sleeve body 2 located in the middle of the axial direction and a first pressure plate 3 and a second pressure plate 4 respectively fixed at both ends of the sleeve body, the first clutch groove 301 is arranged on the inner circle of the first pressure plate 3, and the second clutch groove 401 is arranged on the inner circle of the second pressure plate 4; as shown in the figure, in order to facilitate manufacturing and save manufacturing costs, the transmission sleeve is formed by combining the sleeve body, the first pressure plate and the second pressure plate, and the first pressure plate and the second pressure plate are processed with corresponding clutch grooves and the sleeve body is fixedly assembled to form a whole after the transmission meshing groove is processed; of course, there are many ways of fixed assembly, and the existing mechanical assembly method can be adopted, such as connecting and assembling by bolts distributed in the circumferential direction.

[0049] In this embodiment, a meshing block mounting groove 101 is radially opened on the transmission shaft 1, and the meshing block 5 is installed in the meshing block mounting groove 101 through a spring 7 that applies a radial outward preload force to the meshing block. The setting of the meshing block mounting groove 101 can satisfy the radial sliding of the meshing block 5, and a spring for applying a preload force can be installed at the same time, which will not be repeated here, and the overall installation is convenient.

[0050] In this embodiment, the transmission meshing groove 201, the first clutch groove 301 and the second clutch groove 401 form a groove group, and the groove groups are at least two evenly distributed in the circumferential direction; as shown in the figure, in this embodiment, there are three groove groups evenly distributed in the circumferential direction, which can ensure that the meshing block can smoothly enter the corresponding groove position when the transmission shaft and the transmission sleeve undergo axial relative sliding. At the same time, during idling or overtaking, the meshing block continuously enters and exits the clutch groove, which can reduce the uneven vibration of the meshing block; the meshing blocks 5 are at least two evenly distributed in the circumferential direction, which can ensure the timeliness of the two-way switching transmission.

[0051] In this embodiment, the groove groups are several groups arranged radially opposite to each other, and there are two engaging blocks, namely, engaging block 5 and engaging block 6; the mounting groove is a radial through groove, and the two engaging blocks 5 and 6 are arranged back to back in the mounting groove 101 and the preload force is applied through the two ends of the same spring 7; as shown in the figure, the two engaging blocks 5 and 6 are symmetrically arranged radially in the radially through mounting groove 101, and the spring 7 is located in the mounting groove and applies preload force to the two engaging blocks respectively. The overall structure is simple and practical, and the installation is convenient.

[0052] In this embodiment, the transmission sleeve 2 can be driven to slide axially relative to the transmission shaft 1. In actual use, the transmission sleeve is placed outside the transmission shaft, which is convenient for setting an axial sliding driving structure, such as a general driving structure of a fork and a fork groove, which will not be described in detail here; of course, when in use, the outer circle of the transmission sleeve is usually also provided with a power transmission structure such as a gear, which will not be described in detail here; by driving the transmission sleeve to slide axially, the meshing block is located in the range of the first clutch groove and the transmission meshing groove, or in the range of the second clutch groove and the transmission meshing groove, or in the range of the first clutch groove, the transmission meshing groove and the second clutch groove, thereby completing the required transmission mode;

[0053] The outer circle of the transmission sleeve 2 is fixed with an external gear 15, and the power is output through the external gear 15;

[0054] The outer circumference of the transmission sleeve 2 is also processed with a fork groove, and a driving fork 8 extends into the fork groove to drive the transmission sleeve 2 to slide axially relative to the transmission shaft.

[0055] In this embodiment, the first pressure plate 3 and the second pressure plate 4 are respectively detachably fixedly connected to the sleeve body by bolts evenly distributed in the circumferential direction, forming a detachable structure as a whole. Related parts can be replaced as needed, and the structure has strong versatility.

[0056] In this embodiment, the power input gear pair includes a power input driving gear 10 and a power input driven gear 11 meshing with the power input driving gear 10. The power input driven gear 11 is arranged in transmission cooperation with the transmission shaft 1. The transmission cooperation of the present invention adopts the existing mechanical transmission structure, such as key connection, etc., unless otherwise specified. As shown in the figure, the power input driving gear 10 is arranged in transmission cooperation with a power input shaft 9. Of course, the power received by the power input shaft 9 can come from other speed change mechanisms, which will not be repeated here.

[0057] The power output gear pair includes the outer gear as the power output driving gear and the power output driven gear 13 meshing with the power output driving gear. The outer gear 1 of the transmission sleeve 2 is the power output driving gear. The power output driven gear 13 is arranged on a power output shaft 12 in transmission cooperation. The power output shaft 12 is provided with a terminal output gear 14 in transmission cooperation. The terminal output gear outputs power to the vehicle differential 16. As shown in the figure, the shift fork (arranged on the shift fork shaft) shifts the transmission sleeve to move axially, and the transmission sleeve drives the outer gear to move axially, but maintains constant meshing with the power output driven gear.

[0058] In the present invention, unless otherwise specified, the transmission shaft, transmission sleeve and engagement block are all metal parts. Of course, non-metallic materials with sufficient strength may also be used, which will not be described in detail here.

[0059] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, those skilled in the art should understand that the technical solution of the present invention can be modified or replaced by equivalents without departing from the purpose and scope of the technical solution of the present invention, which should be included in the scope of the claims of the present invention.

Claims

1. A bidirectional transmission, characterized in that: It includes a power input gear pair, a power output gear pair and a bidirectional transmission device located between the power input gear pair and the power output gear pair for transmission, wherein the bidirectional transmission device includes a transmission shaft and a transmission sleeve outermostly disposed on the transmission shaft; The inner circle of the transmission sleeve is provided with a transmission meshing groove, a first clutch groove and a second clutch groove, wherein the first clutch groove and the second clutch groove are arranged at two axial ends of the transmission meshing groove and are both axially connected with the transmission meshing groove; In the circumferential position: One end of the first clutch groove exceeds the transmission meshing groove, and the other end is located within the range of the transmission meshing groove; the second clutch groove exceeds the transmission meshing groove at one end opposite to the first meshing groove in the circumferential direction, and the other end is located within the range of the transmission meshing groove; The transmission shaft is circumferentially transmittable and radially reciprocatingly slidable and is provided with a meshing block; The axial width of the engagement block is greater than the axial width of the transmission engagement groove, and the transmission shaft and the transmission sleeve can be driven to slide relative to each other in the axial direction so that the engagement block is in the axial position: Located in the range of the first clutch slot and the transmission meshing slot, or located in the range of the second clutch slot and the transmission meshing slot, or located in the range of the first clutch slot, the transmission meshing slot, and the second clutch slot; Alternatively, the axial width of the engagement block is equal to or smaller than the axial width of the transmission engagement groove, and the transmission shaft and the transmission sleeve can be driven to slide relative to each other in the axial direction so that the engagement block is in the axial position: within the range of the first clutch groove and the transmission engagement groove, or within the range of the second clutch groove and the transmission engagement groove, or within the range of the transmission engagement groove.

2. The bidirectional transmission according to claim 1, characterized in that: The groove walls at both ends of the first clutch groove and the second clutch groove in the circumferential direction are inclined outward to form a slope that smoothly transitions to the inner circle of the transmission sleeve.

3. The bidirectional transmission according to claim 2, characterized in that: The transmission sleeve includes a sleeve body located in the middle of the axial direction and a first pressure plate and a second pressure plate respectively fixed at two ends of the sleeve body. The first clutch groove is arranged on the inner circle of the first pressure plate, and the second clutch groove is arranged on the inner circle of the second pressure plate.

4. The bidirectional transmission according to claim 3, characterized in that: An engagement block installation groove is radially provided on the transmission shaft, and the engagement block is installed in the engagement block installation groove via a spring that applies a radial outward preload force to the engagement block.

5. The bidirectional transmission according to claim 4, characterized in that: The transmission meshing groove, the first clutch groove and the second clutch groove form a groove group, and the groove groups are at least two and evenly distributed along the circumferential direction; the meshing blocks are at least two and evenly distributed along the circumferential direction.

6. The bidirectional transmission according to claim 5, characterized in that: The groove groups are several groups arranged radially opposite to each other, there are two engaging blocks, the mounting groove is a radial through groove, the two engaging blocks are arranged back to back in the mounting groove and the preload force is applied to them through the two ends of the same spring.

7. The bidirectional transmission according to claim 1, characterized in that: The transmission sleeve can be driven to slide axially relative to the transmission shaft, so that the engagement block is located in the range of the first clutch groove and the transmission engagement groove, or in the range of the second clutch groove and the transmission engagement groove, or in the range of the first clutch groove, the transmission engagement groove and the second clutch groove; The outer circle of the transmission shaft sleeve is fixed with an external gear, and the power is output through the external gear; The outer circle of the transmission sleeve is also processed with a fork groove, and a driving fork extends into the fork groove to drive the transmission sleeve to slide axially relative to the transmission shaft.

8. The bidirectional transmission according to claim 3, characterized in that: The first pressure plate and the second pressure plate are respectively detachably fixedly connected to the shaft sleeve body by bolts evenly distributed in the circumferential direction.

9. The bidirectional transmission according to claim 7, characterized in that: The power input gear pair comprises a power input driving gear and a power input driven gear meshing with the power input driving gear, and the power input driven gear is transmission-matchedly arranged on the transmission shaft; The power output gear pair includes the outer gear as the power output driving gear and the power output driven gear meshing with the power output driving gear. The power output driven gear is transmission-coordinated with a power output shaft, and a terminal output gear is transmission-coordinated with the power output shaft. The terminal output gear outputs power to the vehicle differential.

Images