Gearbox with output shaft clutch and carrying tool

Abstract

The invention relates to a gearbox with an output shaft clutch, which comprises an input shaft and an output shaft, and the output shaft clutch is used for controlling combined transmission or separation between a front output shaft and a rear output shaft. When the output shaft clutch is disengaged and only the motor provides power, transmission mechanisms and hydraulic systems of other parts of the gear box do not work, and noise and vibration are greatly reduced. When the output shaft clutch is combined, the motor and the diesel engine can form a dual-power unit to improve the power of the unit. In order to solve at least one of the technical problems that in the prior art, a gear box is large in noise, large in size, large in weight and the like, the invention provides an output shaft clutch, a gear box and a carrying tool. Combined transmission or separation between the front output shaft and the rear output shaft of the gearbox is achieved through the output shaft clutch.

Description

Technical Field

[0001] The present invention relates to the technical field of gear boxes, and in particular to a gear box with an output shaft clutch and a vehicle. Background Art

[0002] In many fields, with the development of technology and the increase in demand, dual-power power units have gradually developed. For example, in the field of ships and motor vehicles, the power unit usually includes a source engine, a transmission mechanism and a load machine. The source engine is such as a diesel engine, a motor, a steam turbine, etc., the transmission machine is such as a gearbox, a transfer case, a gearbox, etc., and the load machine is such as a propeller. Taking ships as an example, a diesel engine and a motor are used to input power into the gearbox to drive the propeller, thereby forming a power unit. Among them, the diesel engine and the motor can work independently or at the same time. When the diesel engine works independently, the endurance is strong, but the speed is low; when the motor works independently, the speed is high, compared with the diesel engine drive, it is environmentally friendly and has a good quiet effect; when the two work at the same time, they can provide stronger power, for example, see the prior art recorded in the Chinese patent document CN111059263A.

[0003] However, the above-mentioned prior art still has many shortcomings. For example, when only the motor is working, the motor drives the front output shaft to rotate through the transmission gearbox with a hydraulic system, thereby providing power for the propeller. In this working state, the hydraulic system still generates a lot of noise when working and the gearbox is transmitting. In application scenarios with high requirements on noise levels, such as yachts, work boats, etc., it still cannot satisfy users.

[0004] In addition, the size and weight of the gearbox are the primary design difficulties in this field. Many ships, vehicles or other equipment that use gearboxes have limited space and limited load capacity. For example, a large gearbox is not conducive to space utilization, and a large weight is not conducive to energy saving and speed increase of the ship. Especially when the ship is driven by an electric motor, the excessive weight of the gearbox will seriously affect the battery's endurance. Therefore, in the field of gearboxes, minimizing the size and weight of the gearbox is a common technical problem to be solved. Summary of the invention

[0005] In order to solve at least one of the technical problems of the gearbox in the above-mentioned prior art, such as high noise, large size and heavy weight, an embodiment of the present invention proposes a gearbox and a carrier with an output shaft clutch. Through the segmented structural design of the gearbox output shaft, the output shaft clutch is used to realize the coupling transmission or disengagement between the front output shaft and the rear output shaft of the gearbox.

[0006] The technical solution adopted by the present invention to solve the above technical problems is: In a first aspect, the present invention provides an output shaft clutch, which is used to control the coupling or disengagement of the front output shaft and the rear output shaft of the gear box; the output shaft clutch comprises: An output shaft piston, the output shaft piston being slidable axially along the front output shaft, the output shaft piston having a first position and a second position; When the output shaft piston is located at the first position, the output shaft clutch is disengaged, and the front output shaft and the rear output shaft are in a disengaged state. When the output shaft piston is located at the second position, the output shaft clutch is engaged, and the front output shaft and the rear output shaft are in an engaged state.

[0007] The present invention adopts the composition and structural design of the above-mentioned output shaft clutch. The external teeth of the output shaft piston cooperate with the internal teeth of the driven gear and the internal teeth of the rear output shaft. This has high strength and can transmit a large torque after combination. Compared with the clutch in the prior art, the volume and weight of the clutch are greatly reduced. It can be arranged between the driven gear and the rear output shaft, so that the gear box is smaller in volume and lighter in weight, and can transmit large torque, with a simple structure and reliable operation.

[0008] In some achievable embodiments, the output shaft piston has output shaft piston external teeth, and the output shaft piston external teeth are used to mesh with the internal teeth of the driven gear; The driven gear is mounted on the front output shaft and is used to receive power transmitted by the transmission mechanism of the gear box; The rear output shaft has rear output shaft internal teeth, and the rear output shaft internal teeth are used to mesh with the output shaft piston external teeth; When the output shaft piston is in the first position, the output shaft piston outer teeth are meshed with the driven gear inner teeth, and the output shaft piston outer teeth are disengaged from the rear output shaft inner teeth; When the output shaft piston is located at the second position, the external teeth of the output shaft piston are meshed with the internal teeth of the driven gear and the internal teeth of the rear output shaft at the same time.

[0009] The composition and structural design of the output shaft clutch adopted in the present invention have high strength through the mutual cooperation between the external teeth of the output shaft piston and the internal teeth of the driven gear and the internal teeth of the rear output shaft. After the combination, it can transmit a large torque. Compared with the clutch in the prior art, the volume and weight of the clutch are greatly reduced. It can be arranged between the driven gear and the rear output shaft, so that the gear box is smaller in volume and lighter in weight, and can transmit large torque, with a simple structure and reliable operation.

[0010] Some possible implementations also include: An output shaft spring seat, which is arranged on the front output shaft; an output shaft spring, which is arranged between the output shaft spring seat and the output shaft piston; The output shaft piston is located at the first position under the limiting action of the output shaft spring. When the hydraulic system is working, the output shaft piston compresses the output shaft spring under the action of the hydraulic system and reaches the second position.

[0011] Some possible implementations also include: The guide mechanism is arranged between the driven gear and the rear output shaft, and the guide mechanism is used for guiding when the front output shaft is combined with the rear output shaft.

[0012] In some achievable embodiments, the guiding mechanism includes: A guide piston, the guide piston being slidable axially along the front output shaft, the guide piston having a first position and a second position; A rat-tooth disc, the rat-tooth disc is connected to the guide piston, and the rat-tooth disc has rat-tooth disc teeth; A rat-tooth disc seat, the rat-tooth disc seat is arranged on the rear output shaft, the rat-tooth disc seat has rat-tooth disc seat teeth, and the rat-tooth disc seat teeth are used to mesh with the rat-tooth disc teeth; When the guide piston is located at the first position, the hound's tooth disc seat teeth are disengaged from the hound's tooth disc teeth, and when the guide piston is located at the second position, the hound's tooth disc seat teeth are engaged with the hound's tooth disc teeth.

[0013] In some achievable embodiments, the guide mechanism further comprises: A guide plate, the guide plate is arranged on the front output shaft, and the guide plate has guide plate external teeth; The rat-tooth plate has rat-tooth plate inner teeth, which mesh with the guide plate outer teeth to guide the sliding of the rat-tooth plate; And / or, the guide plate has guide plate internal teeth, the front output shaft has front output shaft external teeth, and the guide plate internal teeth are meshed with the front output shaft external teeth.

[0014] In some achievable embodiments, the guide mechanism further comprises: A guide spring, the guide spring being arranged between the guide piston and the guide plate; The guide piston is located at the first position under the limiting action of the guide spring. When the hydraulic system is working, the guide piston compresses the guide spring under the action of the hydraulic system and reaches the second position. And / or, the guide piston has a front end and a rear end, and when the guide piston is in the first position, the front end of the guide piston abuts against the output shaft spring seat, and the rear end of the guide piston is provided with a receiving space; and / or, the main body of the guide spring is at least partially disposed in the accommodation space at the rear end of the guide piston; And / or, the hirth disk is mounted on the rear end surface of the guide piston.

[0015] The guide mechanism adopted by the present invention first makes the hickey plate teeth and the hickey plate seat teeth engage before the output shaft clutch is engaged. Since the guide plate and the hickey plate teeth are pre-positioned with reference to the external teeth of the output shaft piston, the external teeth of the output shaft piston and the internal teeth of the rear output shaft are aligned before meshing through the ingenious cooperation between the various components of the guide mechanism, so that the external teeth of the output shaft piston and the internal teeth of the rear output shaft are smoothly meshed and smoothly engaged, avoiding damage to the components. In a second aspect, the present invention provides a gearbox, the gearbox comprising an input shaft and an output shaft, the output shaft comprising a front output shaft and a rear output shaft; The gearbox further comprises the above-mentioned output shaft clutch, which is used to control the coupling and disengagement of the front output shaft and the rear output shaft; When the diesel engine is used as the power source, the front output shaft and the rear output shaft are connected and driven through the output shaft clutch, and the power is outputted outwards through the input shaft, other transmission components in the gearbox, and the front output shaft and the rear output shaft. When the motor is the only power source, the output shaft clutch is disengaged, the front output shaft and the rear output shaft are disengaged, and only the rear output shaft in the gearbox is connected to the motor shaft; When the diesel engine and the motor provide power at the same time, the front output shaft and the rear output shaft are combined and transmitted through the output shaft clutch, and the rear output shaft in the gear box is connected to the motor shaft.

[0016] The embodiment of the present invention creatively sets the output shaft as a front output shaft and a rear output shaft that are coupled or disengaged by an output shaft clutch, thereby realizing the following working modes: (1) When the diesel engine is the only power source, the front output shaft and the rear output shaft are connected and transmitted through the output shaft clutch, and the power is output to the outside through the input shaft, other transmission components in the gearbox, and the front output shaft and the rear output shaft; (2) When the diesel engine is stopped and only the motor is working, the output shaft clutch is disengaged, the front output shaft and the rear output shaft are disengaged, and only the rear output shaft in the gearbox is connected to the motor shaft. The rear output shaft drives the load machinery to operate, and the forward or reverse rotation of the motor realizes the forward or reverse operation of the vehicle equipped with the above gearbox, such as a ship. Under this working condition, other transmission components and hydraulic systems in the gearbox do not work, which can greatly reduce the noise and vibration of the gearbox; (3) When the diesel engine and the motor provide power at the same time, the front output shaft and the rear output shaft are connected and transmitted through the output shaft clutch. In addition, the rear output shaft in the gearbox is connected to the motor shaft. Since the DC motor can change the speed with the torque, the motor power and the diesel engine power can be superimposed, thereby providing stronger power to the ship; (4) When the diesel engine is working, the motor can also be used as a generator to charge the battery, provide lighting, etc.

[0017] In some achievable embodiments, the front output shaft is coaxially arranged with the rear output shaft; And / or, the front output shaft and the rear output shaft are supported by the same bearing.

[0018] In some achievable embodiments, the front output shaft and the rear output shaft are supported by output shaft bearings; And / or, the output shaft bearing is sleeved on the front output shaft, and the output shaft bearing is embedded in the rear output shaft; And / or, the output shaft bearing is sleeved on the rear output shaft, and the output shaft bearing is embedded in the front output shaft.

[0019] Some possible implementations also include: An input coupling, the input coupling is connected to the input shaft and is used to drive the input shaft to rotate; The input shaft is provided with an input shaft transmission gear, and an idle sleeve of the input shaft is provided with a driving gear; And / or, the forward driving gear can mesh with the driven gear to drive the front output shaft to rotate; And / or, the rear output shaft can be transmission-connected with the motor shaft; And / or, the motor is a DC motor.

[0020] In some implementations, a hydraulic system is also included: The hydraulic system includes a reverse and forward control valve and a working oil circuit; The forward and reverse control valve is used to control the engagement transmission or disengagement of the forward clutch and the reverse clutch; The working oil circuit is used to transport working oil, including a forward working oil circuit arranged in the input shaft, a reverse working oil circuit arranged in the reverse shaft, and a first front output shaft working oil circuit and a second front output shaft working oil circuit arranged in the front output shaft; The oil pump can work under the drive of the input shaft and is used to deliver the working oil to the output shaft clutch and the reverse and forward control valve.

[0021] In some achievable embodiments, the hydraulic system further includes an oil pump, a forward oil inlet sleeve, a reverse oil inlet cap, and an output shaft oil inlet seat; The forward oil inlet sleeve is connected to the reverse forward control valve and is used to input working oil into the forward working oil circuit; The reverse oil inlet cover is connected to the reverse and forward control valve and is used to input working oil into the reverse working oil circuit; The output shaft oil inlet seat is connected to the oil pump and is used to input working oil into the first front output shaft working oil circuit.

[0022] In some practicable embodiments, a cabinet assembly is also included: The box assembly comprises a front box, a rear box and a lower box, and the front box and the rear box are assembled into an upper box; And / or, the upper box body is provided with a joint edge at the matching position between the front box body and the rear box body; And / or, the surface of the lower box body is provided with reinforcing ribs; And / or, the upper box body and the lower box body are fixed by flange cooperation.

[0023] In a third aspect, the present invention provides a vehicle, comprising the above-mentioned gear box; And / or, the vehicle is a ship.

[0024] 1. In the embodiment of the present invention, the output shaft of the gearbox is divided into a front output shaft and a rear output shaft, and an output shaft clutch is arranged between the front output shaft and the rear output shaft of the gearbox. When the output shaft clutch is engaged, the power provided by the external power source diesel engine can be transmitted to the load machinery, such as a propeller, etc., and under the control of the forward and reverse control valve, the ship, vehicle, etc. can be moved forward or reversed; When the output shaft clutch is engaged, the rear output shaft is connected to the motor shaft, and the motor can also be started to work, so that the power provided by multiple power sources is superimposed to output stronger power; when the output shaft clutch is disengaged, the motor does not drive the load mechanism through the gear box, and works according to the requirements of the forward and reverse working conditions. Only driven by the motor, the forward and reverse rotation of the motor is used to control the forward or reverse movement of ships and vehicles. At this time, the power output of the motor has nothing to do with the front output shaft, output shaft transmission gear, driven gear, forward driving gear / reverse driving gear, forward transmission gear / reverse transmission gear, and various friction plates. Under this working condition, these transmission components do not work, which greatly reduces noise and vibration.

[0025] 2. Preferably, the composition and structural design of the output shaft clutch adopted in the embodiment of the present invention has high strength through the cooperation between the external teeth of the output shaft piston and the internal teeth of the driven gear and the internal teeth of the rear output shaft. After the combination, it can transmit a large torque. Compared with the clutch in the prior art, the volume and weight of the clutch are greatly reduced, and it can be arranged between the driven gear and the rear output shaft, so that the gearbox is smaller in size and lighter in weight, and can transmit large torque, with a simple structure and reliable operation.

[0026] 3. Preferably, the guide mechanism adopted in the embodiment of the present invention first engages the hickey plate teeth and the hickey plate seat teeth before the output shaft clutch is engaged. Since the guide plate and the hickey plate teeth are pre-positioned with reference to the external teeth of the output shaft piston, through the ingenious cooperation between the various components of the guide mechanism, the external teeth of the output shaft piston are aligned with the internal teeth of the rear output shaft before they are meshed, so that the external teeth of the output shaft piston and the internal teeth of the rear output shaft can be smoothly meshed and combined to avoid damage to the components.

[0027] 4. Preferably, in the embodiment of the present invention, the input coupling and the input shaft transmission gear are connected in transmission by meshing, and the torque transmitted from the external power source is not transmitted through the input shaft, but is directly input into the input shaft transmission gear. When the input shaft transmission gear is combined with the driving gear of the vehicle, the power transmission route is the shortest.

[0028] 5. Preferably, in the embodiment of the present invention, when the front output shaft and the rear output shaft are supported by the same bearing, the structure is simple, can meet the support requirements of the shaft, has a small size, light weight, clear support points, and strong reliability.

[0029] 6. Preferably, the embodiment of the present invention uses two rolling bearings and one thrust ball bearing to support the output shaft and the input shaft, and decomposes the axial force of the gear and the radial force of the gear and uses different bearings to bear them. The two rolling bearings bear the radial force of the gear, and the one thrust ball bearing bears the axial force of the gear. This solves the technical problems of poor force bearing capacity and short life of the rolling bearings, so that the input shaft and the reverse shaft can use rolling bearings, thereby reducing the weight of the gear box, and has a simple structure and reliable use.

[0030] 7. Preferably, the housing assembly of the embodiment of the present invention is assembled into a complete housing by assembling a front housing, a rear housing and a lower housing, which improves the convenience of assembly and disassembly of the gear box and facilitates mass production. The rigidity of the housing is improved by using joint edges, reinforcing ribs and fixing the upper and lower housings with flanges. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] Figure 1 A schematic structural diagram of a gearbox according to an embodiment of the present invention; Figure 2 for Figure 1 DD sectional view schematically showing the composition and structure of the input shaft assembly and the output shaft assembly; Figure 3 for Figure 1 The CC cross-sectional view schematically shows the composition and structure of the input shaft assembly; Figure 4 for Figure 1 The BB cross-sectional view schematically shows the composition and structure of the output shaft assembly; Figure 5 for Figure 1 AA sectional view schematically showing the composition and structure of the reverse axle assembly; Figure 6 It is a partially enlarged schematic diagram of the output shaft clutch and the guide mechanism in the embodiment of the present invention, schematically showing the composition and structure of the output shaft clutch; Figure 7Another partially enlarged schematic diagram of the output shaft clutch and the guide mechanism in the embodiment of the present invention; Figure 8 It is a three-dimensional composition and structural schematic diagram of the output shaft clutch and the guide mechanism in the embodiment of the present invention; Fig. 9 It is a three-dimensional structural schematic diagram of a box assembly in an embodiment of the present invention; Fig.10 It is a cross-sectional view of the box assembly in an embodiment of the present invention.

[0032] Description of reference numerals: Input coupling 1, input shaft transmission gear 2, first rolling bearing 3, input shaft 4, follow-up piston 5, follow-up spring 6, first outer friction plate 7, first inner friction plate 8, follow-up driving gear 9; The second rolling bearing 10, the first rolling bearing seat 11, the first thrust ball bearing 12, the input shaft seat 13, the oil inlet sleeve 14, the oil pump coupling 15, the oil pump 16, the sixth bearing 17, the seventh bearing 18, and the output coupling 19; Rear output shaft 20, output shaft bearing 21, guide plate 22, Hirth plate seat 23, Hirth plate 24, guide piston 25, output shaft spring seat 26, positioning ring 27, output shaft spring 28, output shaft piston 29; Driven gear 30, front output shaft 31, output shaft oil inlet seat 32, fifth bearing 33, third rolling bearing 34, reverse transmission gear 35, second outer friction plate 36, second inner friction plate 37, reverse driving gear 38, fourth rolling bearing 39; A second thrust ball bearing 40, a reverse oil inlet cover 41, a reverse shaft 42, a reverse shaft seat 43, a second rolling bearing seat 44, a box assembly 45, a reverse spring seat 46, a reverse spring 47, a reverse piston 48, and a front box 49; Reverse and forward control valve 50, rear box body 51, lower box body 52, guide spring 53, forward clutch 54, reverse clutch 55, output shaft clutch 56, clutch seat 57 of forward driving gear end, clutch seat 58 of reverse driving gear end, forward working oil circuit 59; Reverse working oil circuit 60 , first front output shaft working oil circuit 61 , second front output shaft working oil circuit 62 . DETAILED DESCRIPTION

[0033] To make the purpose, technical solution and advantages of the present invention more clearly understood, the present invention is further described in detail below in conjunction with specific embodiments and with reference to the accompanying drawings. However, those skilled in the art will appreciate that the present invention is not limited to the accompanying drawings and the following embodiments.

[0034] In a first aspect, an embodiment of the invention provides an output shaft clutch for controlling the coupling or disengagement between the front output shaft 31 and the rear output shaft 20 of the gearbox. Figure 2 , Figure 4 as well as Figure 6-Figure 8 In one embodiment, the output shaft clutch 56 comprises: An output shaft piston 29, wherein the outer wall of the output shaft piston 29 has output shaft piston outer teeth, the output shaft piston 29 can slide axially along the front output shaft 31, and the output shaft piston 29 has a first position and a second position; The driven gear 30 has driven gear internal teeth, which can mesh with the output shaft piston external teeth; the rear output shaft 20 has rear output shaft internal teeth, which can mesh with the output shaft piston external teeth; When the output shaft piston 29 is located in the first position, the output shaft clutch 56 is disengaged, at which time the outer teeth of the output shaft piston are disengaged from the inner teeth of the rear output shaft, and the front output shaft 31 and the rear output shaft 20 are in a disengaged state; when the output shaft piston 29 is located in the second position, the output shaft clutch 56 is engaged, at which time the outer teeth of the output shaft piston are engaged with the inner teeth of the driven gear and the inner teeth of the rear output shaft at the same time.

[0035] In a specific embodiment, the rear end of the driven gear 30 has a driven gear annular wall, the inner surface of the driven gear annular wall is provided with driven gear internal teeth, and the output shaft piston 29 has an output shaft piston annular wall, and the outer surface of the output shaft piston annular wall is provided with output shaft piston external teeth. For example, the front end of the rear output shaft 20 has a rear output shaft annular wall, and the inner surface of the rear output shaft annular wall is provided with internal teeth. The driven gear annular wall is arranged opposite to the rear output shaft annular wall. The output shaft piston 29 is slidably sleeved on the front output shaft 31.

[0036] Preferably, when the output shaft piston 29 is located at the first position, the external teeth of the output shaft piston are meshed with the internal teeth of the driven gear. Figure 2 , 4 , 6-8, in one embodiment, the output shaft clutch 56 further includes: The output shaft spring seat 26 is fixedly mounted on the front output shaft 31; The output shaft spring 28 is arranged between the output shaft spring seat 26 and the output shaft piston 29. The output shaft piston 29 is located at the first position under the limiting action of the output shaft spring 28. When the hydraulic system is working, the output shaft piston 29 compresses the output shaft spring 28 under the action of the hydraulic system and reaches the second position.

[0037] Preferably, the output shaft spring seat 26 is fixedly mounted on the front output shaft 31 via a positioning ring 27. The positioning ring 27 is fixed on the front output shaft 31, and the output shaft spring seat 26 is fixed on the positioning ring 27. The positioning ring 27, for example, is composed of two half rings.

[0038] The front output shaft 31 is provided with a first front output shaft working oil passage 61 , and the first front output shaft working oil passage 61 is used to transport working oil that pushes the output shaft piston 29 to move toward the second position.

[0039] In a specific embodiment, the main body of the output shaft spring 28 is at least partially located in the annular wall of the output shaft piston, one end of the output shaft spring 28 abuts against the inner bottom surface of the output shaft piston, and the other end abuts against the output shaft spring seat 26. Under the action of the output shaft spring 28, the output shaft piston 29 is located in the first position. At this time, the external teeth of the output shaft piston are disengaged from the internal teeth of the rear output shaft and only mesh with the internal teeth of the driven gear.

[0040] When the hydraulic system is working, under the pressure of the working oil, the output shaft piston 29 compresses the output shaft spring 28, and the output shaft piston 29 slides along the front output shaft 31 toward the rear output shaft 20 and enters the rear output shaft 20, so that a part of the output shaft piston outer teeth remain engaged with the driven gear inner teeth, while the other part is engaged with the rear output shaft inner teeth. As a result, the output shaft piston outer teeth are engaged with the driven gear inner teeth and the rear output shaft inner teeth at the same time, and the front output shaft 30 and the rear output shaft 20 are in a combined state. At this time, the output shaft piston 29 is in the second position.

[0041] The positioning ring 27 is also used to limit the stroke of the output shaft piston 29. In a specific embodiment, the inner bottom surface of the output shaft piston 29 is also provided with a positioning portion, and the positioning portion corresponds to the positioning ring 27. When the output shaft piston 29 slides toward the rear output shaft 20 under the action of the hydraulic system, the output shaft piston 29 stops sliding when the positioning portion abuts against the positioning ring 27. The output shaft piston 29 has an outer bottom surface, and there is a gap between the outer bottom surface and the bottom surface of the driven gear. The working oil can enter the gap through the first front output shaft working oil circuit 61 provided on the front output shaft 31, and the pressure acts on the outer bottom surface of the output shaft piston 29, thereby pushing the output shaft piston 29 to slide toward the rear output shaft 20.

[0042] refer to Figure 2 , 4 , 6-8, in one embodiment, the gearbox further comprises: The guide mechanism is used to guide the front output shaft 31 and the rear output shaft 20 when they are combined so that the two can be combined smoothly.

[0043] In one embodiment, the guide mechanism is disposed between the driven gear 30 and the rear output shaft 20 .

[0044] The guide mechanism provides guidance, so that the front output shaft 31 and the rear output shaft 20 can be smoothly coupled, thereby avoiding damage to components during coupling.

[0045] In one embodiment, the guiding mechanism comprises: A guide piston 25, wherein the guide piston 25 can slide axially along the front output shaft 31, and the guide piston 25 has a first position and a second position; The hound's tooth disk 24 is fixed on the guide piston 25, and the rear end face of the hound's tooth disk 24 has hound's tooth teeth, and the hound's tooth disk 24 has hound's tooth internal teeth; preferably, the hound's tooth teeth are hound's tooth end face teeth, which are arranged on the end face of the hound's tooth disk.

[0046] A guide plate 22, wherein the guide plate 22 is fixed on the front output shaft 31; preferably, the guide plate 22 has guide plate internal teeth, and the front output shaft 31 has front output shaft external teeth, and the guide plate internal teeth are meshed and fixed with the front output shaft external teeth; The guide plate 22 has outer teeth of the guide plate, and the inner teeth of the rat-tooth plate mesh with the outer teeth of the guide plate, so as to guide the rat-tooth plate 24 when it slides; The rat-tooth disc seat 23 is fixed on the rear output shaft 20, and the front end face of the rat-tooth disc seat 23 has rat-tooth disc seat teeth, and the rat-tooth disc seat teeth can engage with the rat-tooth disc teeth; preferably, the rat-tooth disc seat teeth are rat-tooth disc seat end face teeth, which are arranged on the end face of the rat-tooth disc seat.

[0047] When the guide piston 25 is located at the first position, the hirth disc seat teeth are disengaged from the hirth disc teeth, and when the guide piston 25 is located at the second position, the hirth disc seat teeth are meshed with the hirth disc teeth.

[0048] In one embodiment, the guiding mechanism further comprises: A guide spring 53 is provided between the guide piston 25 and the guide plate 22 .

[0049] The guide piston 25 is located at the first position under the action of the guide spring 53 . The guide piston 25 is located at the second position by compressing the guide spring 53 under the action of the hydraulic system.

[0050] Preferably, the front output shaft 31 is provided with a first front output shaft working oil circuit 61 , and the first front output shaft working oil circuit 61 is also used to transport working oil for pushing the guide piston 25 to move to the second position.

[0051] In a specific embodiment, there is an accommodation space between the output shaft spring seat 26 and the front output shaft 31, the guide piston 25 is at least partially disposed in the accommodation space, and the guide piston 25 is slidably sleeved on the front output shaft 31. The guide piston 25 has a front end and a rear end, and when the guide piston 25 is in the first position, the front end of the guide piston abuts against the inner wall of the output shaft spring seat 26 opposite to the front output shaft 31, and the rear end of the guide piston is provided with an accommodation space, and the main body of the guide spring 53 is at least partially disposed in the accommodation space.

[0052] The rear end of the guide piston is fixedly installed with the houndstooth disc 24, which is annular and has a front end face, a rear end face and an inner wall face. The inner wall face of the houndstooth disc 24 is provided with houndstooth inner teeth, and the rear end face of the houndstooth disc is provided with houndstooth end face teeth. There is a accommodating space between the houndstooth disc 24 and the front output shaft 31; the guide disc 22 is at least partially arranged in the accommodating space, the guide disc 22 is annular and fixedly installed on the front output shaft 31, and the outer surface of the guide disc 22 is provided with guide disc outer teeth, and the houndstooth inner teeth and the guide disc outer teeth are meshed.

[0053] When the guide piston 25 slides toward the rear output shaft 20 and pushes the hickey disc 24 to slide, the guide disc 22 is used to guide the hickey disc 24, and the inner surface of the guide disc 22 is provided with guide disc inner teeth, and the outer surface of the front output shaft 31 is provided with front output shaft outer teeth, and the guide disc inner teeth are meshed and fixed with the front output shaft outer teeth; the hickey disc seat 23 is annular and fixedly installed on the inner end surface of the rear output shaft 20, and the hickey disc seat 23 has a front surface, and the front surface of the hickey disc seat is provided with hickey disc seat end face teeth, and the hickey disc seat end face teeth can mesh with the hickey disc end face teeth; one end of the guide spring 53 abuts against the guide piston 25, and the other end abuts against the guide disc 22. Under the action of the guide spring 53, the guide piston 25 is located in the first position, at which time, the hickey disc teeth are disengaged from the hickey disc seat end face teeth.

[0054] When the hydraulic system is working, under the pressure of the working oil, the guide piston 25 compresses the guide spring 53, and the guide piston 25 slides along the front output shaft 31 toward the rear output shaft 20, pushing the hickey plate 24 to slide toward the hickey plate seat 23 under the guidance of the guide plate 22, so that the end face teeth of the hickey plate and the end face teeth of the hickey plate seat are engaged. At this time, the guide piston 25 is in the second position.

[0055] The guide piston 25 has an outer bottom surface, and there is a gap between the outer bottom surface and the output shaft spring seat 26. The working oil can enter the gap through the first front output shaft working oil circuit 61 arranged on the front output shaft 31, so that the pressure acts on the outer bottom surface of the guide piston 25, thereby pushing the guide piston 25 to slide in the direction of the rear output shaft 20, and then pushing the hirth plate 24 to slide in the direction of the rear output shaft 20.

[0056] Since the inner teeth of the guide plate are fixedly engaged on the front output shaft, the outer teeth of the guide plate are engaged with the inner teeth of the hickey plate, so that the hickey plate 24 is positioned with the front output shaft 31; when the guide piston 25 moves, it pushes the hickey plate 24 to move, so that the end face teeth of the hickey plate are engaged with the end face teeth of the hickey plate seat fixed on the rear output shaft 20. Since the guide plate and the end face teeth of the hickey plate are pre-positioned with reference to the outer teeth of the output shaft piston, after the hickey plate is engaged with the hickey plate seat, the inner teeth of the driven gear are aligned with the inner teeth of the rear output shaft, so that the outer teeth of the output shaft piston can smoothly engage with the inner teeth of the driven gear and the inner teeth of the rear output shaft at the same time.

[0057] In the prior art, gearboxes generally have a fixed reduction ratio, the most common being 3:1. When the input torque is 10,000 Nm, the transmitted torque reaches 30,000 Nm. In the prior art, in order to transmit a large torque of 30,000 Nm, a hydraulic clutch is generally used. The hydraulic clutch used is bulky, and the weight of the clutch even accounts for most of the weight of the gearbox. The embodiment of the present invention adopts the composition and structural design of the above-mentioned output shaft clutch 56. The external teeth of the output shaft piston cooperate with the internal teeth of the driven gear and the internal teeth of the rear output shaft. This mode has high strength, and can transmit a large torque after combination. Compared with the clutch in the prior art, the volume and weight of the clutch are greatly reduced, and it can be set between the driven gear 30 and the rear output shaft 20, so that the gearbox is smaller in volume and lighter in weight, and can transmit a large torque, with a simple structure and reliable operation.

[0058] In addition, the present invention adopts the above-mentioned guide mechanism, and utilizes the same first front output shaft working oil circuit 61 set on the front output shaft 31 to transport the working oil that pushes the output shaft piston 29 and the guide piston 25 to slide in the direction of the rear output shaft 20, by making the cylinder volume of the guide piston 25 smaller than the cylinder volume of the output shaft piston 29.

[0059] In some feasible embodiments, the elastic force of the guide spring 53 is smaller than the elastic force of the output shaft spring 28, and the guide piston 25 moves faster when the working oil is input. For example, the guide piston 25 can move nearly 10 mm by moving the output shaft piston 29 by 1 mm of oil. Therefore, the guide piston 25 first combines the hickey disc teeth and the hickey disc seat teeth. Since the guide disc and the hickey disc teeth are pre-positioned with reference to the outer teeth of the output shaft piston, through the ingenious cooperation between the inner teeth of the hickey disc, the outer teeth of the guide disc, the hickey disc teeth, and the hickey disc seat teeth, the outer teeth of the output shaft piston and the inner teeth of the rear output shaft are aligned before they are meshed, so that the outer teeth of the output shaft piston and the inner teeth of the rear output shaft can be smoothly meshed and combined to avoid damage to components.

[0060] Second, reference Figure 1-10 , an embodiment of the present invention provides a gear box, the gear box comprising: An input shaft 4, which can rotate under the drive of a first power device, such as a diesel engine; Output shafts, including a front output shaft 31 and a rear output shaft 20; The output shaft clutch 56 is used to control the transmission connection or disconnection between the front output shaft 31 and the rear output shaft 20 .

[0061] The rear output shaft 20 can be connected to the motor shaft in a transmission manner. Preferably, the motor is a DC motor, which can realize forward or reverse rotation of the motor shaft.

[0062] The rear output shaft 20 is connected to a load machine, such as a propeller.

[0063] The embodiment of the present invention innovatively sets the output shaft as the front output shaft 31 and the rear output shaft 20 which are connected or disengaged by the output shaft clutch 56, thereby realizing the following working modes: (1) when only the diesel engine provides power, the front output shaft 31 and the rear output shaft 20 are connected and transmitted through the output shaft clutch 56, and the power is output to the outside through the input shaft 4, other transmission components in the gearbox, and the front output shaft 31 and the rear output shaft 20; (2) when the diesel engine is stopped and only the motor is working, the output shaft clutch 56 is disengaged, the front output shaft 31 and the rear output shaft 20 are disengaged, and only the rear output shaft 20 in the gearbox is connected to the motor shaft, and the rear output shaft 20 drives the load machinery to operate, and the forward or reverse operation of the vehicle equipped with the above-mentioned gearbox is realized through the forward or reverse rotation of the motor, and the vehicle is, for example, a ship. Under this working condition, other transmission components and hydraulic systems in the gearbox do not work, which can greatly reduce the noise and vibration of the gearbox; (3) When the diesel engine and the motor provide power at the same time, the front output shaft 31 and the rear output shaft 20 are connected and transmitted through the output shaft clutch 56. In addition, the rear output shaft 20 in the gearbox is connected to the motor shaft. Since the DC motor can change the speed with the torque, the motor power can be superimposed on the diesel engine power, thereby providing stronger power for the ship; (4) When the diesel engine is working, the motor can also be used as a generator to charge the battery, provide lighting, etc.

[0064] refer to Figure 2 and Figure 4 In one embodiment, the gearbox further comprises: An input shaft transmission gear 2, fixedly mounted on the input shaft 4, for receiving power output from the first power device; The driven gear 30 is fixed on the front output shaft 31 and is used to receive the power transmitted from the input shaft transmission gear 2 through the transmission mechanism; The front output shaft 31 and the rear output shaft 20 are coaxially arranged, and the two can rotate relative to each other when they are disengaged; The output shaft clutch 56 is disposed between the driven gear 30 and the rear output shaft 20 .

[0065] refer to Figure 2 , 4 In one embodiment, the front output shaft 31 and the rear output shaft 20 are supported by the same bearing. For example, the front end of the rear output shaft 20 has a rear output shaft annular wall, the rear output shaft annular wall encloses a hollow portion, and the output shaft bearing 21 is disposed in the rear output shaft 20, for example, in the hollow portion, thereby, the rear end of the front output shaft 31 is supported in the rear output shaft 20 through the output shaft bearing 21, thereby, the front output shaft 31 and the rear output shaft 20 are supported by the output shaft bearing 21.

[0066] The front output shaft 31 and the rear output shaft 20 are supported by the same bearing, which has a simple structure, can meet the support requirements of the shaft, has a small size, is light in weight, has a clear support point, and has high reliability.

[0067] In one embodiment, the input shaft transmission gear 2 is hollow in structure and has a receiving space, and the front end of the input shaft 4 is fixed in the receiving space; the on-board driving gear 9 is loosely mounted on the input shaft 4; the on-board clutch 54 is used to control the transmission engagement or disengagement between the input shaft transmission gear 2 and the on-board driving gear 9, wherein the on-board clutch 54 includes a on-board piston 5, a on-board spring 6, a first outer friction plate 7 and a first inner friction plate 8.

[0068] The input shaft transmission gear 2 includes a front end portion with a first outer diameter and a rear end portion with a second outer diameter, and a step is formed at the hollow structure thereof, thereby the rear end portion of the input shaft transmission gear has an inner bottom surface, and the rear end portion of the input shaft transmission gear 2 has an annular wall structure, and a pressure plate is fixed on the rear end surface of the annular wall, thereby forming an accommodating space between the pressure plate and the inner bottom surface of the rear end portion of the input shaft transmission gear, and the following piston 5, the first outer friction plate 7 and the first inner friction plate 8 are arranged in the accommodating space, and the first outer friction plate 7 and the first inner friction plate 8 are located between the following piston 5 and the pressure plate at the rear end of the input shaft transmission gear 2; the inner teeth of the first outer friction plate 7 and the first inner friction plate 8 are meshed with the following driving gear 9.

[0069] The front end of the follow-up driving gear 9 is a hollow structure with a accommodating space. The clutch seat 57 at the follow-up driving gear end and the main body of the follow-up spring 6 are at least partially arranged in the accommodating space. One end of the follow-up spring 6 abuts against the follow-up piston 5, and the other end abuts against the clutch seat 57 at the follow-up driving gear end.

[0070] There is a gap between the front end surface of the follow-up piston 5 and the inner bottom surface of the rear end portion of the input shaft transmission gear 2. The input shaft 4 has a follow-up working oil passage 59 connected to the gap. The working oil can enter the gap through the follow-up working oil passage 59 to transmit pressure to the follow-up piston 5.

[0071] The follow-up piston 5 is located in the first position under the action of the follow-up spring 6, at this time, the follow-up clutch 54 is disengaged; the follow-up piston 5 compresses the follow-up spring 6 under the action of the hydraulic system, so that the follow-up piston 5 is located in the second position, pressing the first outer friction plate 7 and the first inner friction plate 8, at this time, the follow-up clutch 54 is engaged, and the input shaft drive gear 2 and the follow-up driving gear 9 are combined for transmission.

[0072] refer to Figure 2-4 In one embodiment, the gearbox further comprises: an input shaft transmission gear 2 fixed to the input shaft 4, the input shaft transmission gear 2 being used to receive power output from the first power device; A driving gear 9 for the following vehicle, wherein the driving gear 9 for the following vehicle is loosely sleeved on the input shaft 4; The driven gear 30 has external teeth, and the driving gear 9 meshes with the external teeth of the driven gear; The on-drive clutch 54 is used to control the transmission connection or disconnection between the input shaft transmission gear 2 and the on-drive driving gear 9 .

[0073] Preferably, the input shaft transmission gear 2 is of a hollow structure and has a receiving space, and the input shaft 4 is fixed in the receiving space.

[0074] In one embodiment, the fly-by clutch 54 is a hydraulic wet multi-plate friction clutch.

[0075] In one embodiment, the freewheeling clutch 54 comprises: A shunting piston 5, wherein the shunting piston 5 can slide along the input shaft 4, and the shunting piston 5 has a first position and a second position; When the on-board piston 5 is located at the first position, the input shaft transmission gear 2 and the on-board driving gear 9 are disengaged. When the on-board piston 5 is located at the second position, the input shaft transmission gear 2 and the on-board driving gear 9 are combined for transmission.

[0076] In one embodiment, the on-drive clutch 54 further includes: The clutch seat 57 at the driving gear end of the vehicle is arranged at the front end of the driving gear 9 of the vehicle, and has external teeth of the clutch seat of the vehicle; The first outer friction plate 7 and the first inner friction plate 8, the first outer friction plate 7 and the first inner friction plate 8, the first outer friction plate 7 has first outer friction plate outer teeth, the first inner friction plate 8 has first inner friction plate inner teeth, the input shaft transmission gear 2 has input shaft transmission gear inner teeth, the first outer friction plate outer teeth mesh with the input shaft transmission gear inner teeth, the first inner friction plate inner teeth mesh with the forward clutch seat outer teeth; the first outer friction plate 7 and the first inner friction plate 8 are compressed under the action of the working oil to make the input shaft transmission gear 2 and the forward driving gear 9 combined for transmission; A pressure plate is fixed to the rear end of the input shaft transmission gear 2, and the first outer friction plate 7 and the first inner friction plate 8 are arranged between the following piston 5 and the pressure plate at the rear end of the input shaft transmission gear 2; The following spring 6 is arranged between the following piston 5 and the clutch seat 57 at the following driving gear end.

[0077] The follow-up piston 5 is located in the first position under the action of the follow-up spring 6. Under the action of the hydraulic system, the follow-up piston 5 compresses the follow-up spring 6, and the follow-up piston 5 moves toward the rear end of the input shaft 4 to the second position. When the follow-up piston 5 is in the second position, the rear end surface of the follow-up piston 5, the first outer friction plate 7, the first inner friction plate 8 and the inner surface of the pressure plate at the rear end of the input shaft transmission gear are subjected to external pressure and are pressed and engaged with each other, so that when the input shaft transmission gear 2 rotates, it can drive the first outer friction plate 7 and the first inner friction plate 8 to rotate, and then drive the follow-up driving gear 9 to rotate, and finally drive the driven gear 30 to rotate.

[0078] In a specific embodiment, the input shaft transmission gear 2 is a hollow structure, including a front end portion having a first outer diameter and a rear end portion having a second outer diameter, and a step is formed at the hollow structure, thereby, the rear end portion of the input shaft transmission gear has an inner bottom surface, and the rear end portion of the input shaft transmission gear 2 has an annular wall structure, and a pressure plate is fixed on the rear end surface of the annular wall, thereby forming an accommodating space between the pressure plate and the inner bottom surface of the rear end portion of the input shaft transmission gear, and the following piston 5, the first outer friction plate 7 and the first inner friction plate 8 are arranged in the accommodating space.

[0079] The following car driving gear 9 is also meshed with the external teeth of the driven gear; the front end portion of the following car driving gear 9 is a hollow structure and has a accommodating space, and the main body of the following car spring 6 is at least partially arranged in the accommodating space, one end of the following car spring 6 abuts against the following car piston 5, and the other end abuts against the clutch seat 57 at the following car driving gear end arranged on the following car driving gear 9 in the accommodating space.

[0080] There is a gap between the front end surface of the follow-up piston 5 and the inner bottom surface of the rear end portion of the input shaft transmission gear 2. The input shaft 4 has a follow-up working oil circuit 59. The follow-up working oil circuit 59 is used to transport working oil that pushes the follow-up piston 5 to move to the second position. The follow-up working oil circuit 59 is connected to the gap. The working oil can enter the gap through the follow-up working oil circuit 59 to transmit pressure to the follow-up piston 5, so that the follow-up piston 5 moves toward the rear end direction of the input shaft 4 to the second position, thereby compressing the first outer friction plate 7 and the first inner friction plate 8.

[0081] refer to Figure 2-4 In one embodiment, the gearbox further comprises: The input coupling 1 is used to receive power output from a first power device, wherein the first power device is, for example, a diesel engine, and a flywheel of the diesel engine is connected to the input coupling 1, thereby providing power to the gearbox.

[0082] refer to Figure 2-4 In one embodiment, the gearbox further comprises: The output coupling 19 is fixedly mounted on the rear output shaft 20 and is used for outputting power outwards. The output coupling 19 is drivingly connected to the rear output shaft 20 .

[0083] refer to Figure 2 , 5 In one embodiment, the gearbox further comprises: A reverse shaft 42, the reverse transmission gear 35 is fixed on the reverse shaft 42, and the input shaft transmission gear 2 is meshed with the reverse transmission gear 35; The reverse driving gear 38 is loosely sleeved on the reverse shaft 42 , and the reverse driving gear 38 is meshed with the outer teeth of the driven gear; the reverse clutch 55 is used to control the coupling transmission or disengagement between the reverse transmission gear 35 and the reverse driving gear 38 .

[0084] In one embodiment, the reverse clutch 55 is a hydraulic wet multi-plate friction clutch.

[0085] In one embodiment, the reverse clutch 55 comprises: a reverse piston 48 , wherein the reverse piston 48 is capable of sliding along the reverse shaft 42 , and the reverse piston 48 has a first position and a second position; When the reverse piston 48 is located at the first position, the reverse transmission gear 35 and the reverse driving gear 38 are disengaged, and when the reverse piston 48 is located at the second position, the reverse transmission gear 35 and the reverse driving gear 38 are combined for transmission.

[0086] In one embodiment, the reverse clutch 55 further comprises: The clutch seat 58 at the reverse driving gear end is arranged at the front end of the reverse driving gear 38 and has a reverse clutch seat outer tooth; a second outer friction plate 36 and a second inner friction plate 37, wherein the second outer friction plate 36 has second outer friction plate outer teeth, the second inner friction plate 37 has second inner friction plate inner teeth, the reverse transmission gear 35 has reverse transmission gear inner teeth, the second outer friction plate outer teeth mesh with the reverse transmission gear inner teeth, and the second inner friction plate inner teeth mesh with the reverse clutch seat outer teeth; A pressure plate is fixed to the rear end of the reverse transmission gear 35, and the second outer friction plate 36 and the second inner friction plate 37 are arranged between the reverse piston 48 and the pressure plate at the rear end of the reverse transmission gear 35; A reverse spring seat 46 is disposed at the front end of the reverse driving gear 38; The reverse spring 47 is disposed between the reverse piston 48 and the reverse spring seat 46 .

[0087] The reverse piston 48 is located in the first position under the action of the reverse spring 47. Under the action of the hydraulic system, the reverse piston 48 compresses the reverse spring 47, and the reverse piston 48 moves toward the rear end direction of the reverse shaft 42 to the second position. When the reverse piston 48 is in the second position, the rear end surface of the reverse piston 48, the second outer friction plate 36, the second inner friction plate 37 and the inner surface of the pressure plate at the rear end of the reverse transmission gear 35 are subjected to external pressure and are pressed and engaged with each other, so that when the reverse transmission gear 35 rotates, it can drive the second outer friction plate 36 and the second inner friction plate 37 to rotate, thereby driving the reverse driving gear 38 to rotate, and finally driving the driven gear 30 to rotate.

[0088] In a specific embodiment, the reverse transmission gear 35 is a hollow structure, including a front end portion with a first outer diameter and a rear end portion with a second outer diameter, and a step is formed at the hollow structure, thereby, the rear end portion of the reverse transmission gear 35 has an inner bottom surface, and the rear end portion of the reverse transmission gear 35 has an annular wall structure, and a pressure plate is fixed on the rear end surface of the annular wall, so that an accommodation space is formed between the pressure plate and the inner bottom surface of the rear end portion of the reverse transmission gear 35, and the second outer friction plate 36 and the second inner friction plate 37 are arranged in the accommodation space; The reverse driving gear 38 is also meshed with the outer teeth of the driven gear; the front end of the reverse driving gear 38 is a hollow structure, having a receiving space, and the main body of the reverse spring 47 is at least partially arranged in the receiving space, one end of the reverse spring 47 abuts against the reverse piston 48, and the other end abuts against the reverse spring seat 46 arranged on the reverse driving gear 38 in the receiving space.

[0089] There is a gap between the front end surface of the reverse piston 48 and the inner bottom surface of the rear end portion of the reverse transmission gear 35. The reverse shaft 42 has a reverse working oil circuit 60. The reverse working oil circuit 60 is used to transport working oil that pushes the reverse piston 48 to move to the second position. The reverse working oil circuit 60 is connected to the gap. The working oil can enter the gap through the reverse working oil circuit 60 to transmit pressure to the reverse piston 48, so that the reverse piston 48 moves toward the rear end direction of the reverse shaft 42 to the second position, thereby compressing the second outer friction plate 36 and the second inner friction plate 37.

[0090] refer to Figure 1-5 In one embodiment, the gearbox further comprises a hydraulic system: The hydraulic system includes a forward and reverse control valve 50, an oil pump 16, a working oil circuit, a forward oil inlet sleeve 14, a reverse oil inlet cover 41, and an output shaft oil inlet seat 32; The forward and reverse control valve 50 is used to control the engagement or disengagement of the forward clutch 54 and the reverse clutch 55; The oil pump 16 is connected to the rear end of the input shaft 4 through the oil pump coupling 15, and rotates coaxially with the input shaft 4, and is used to deliver the working oil to the output shaft clutch 56 and the reverse control valve 50; The working oil circuit includes a forward working oil circuit 59 provided in the input shaft 4, a reverse working oil circuit 60 provided in the reverse shaft 42, and a first front output shaft working oil circuit 61 and a second front output shaft working oil circuit 62 provided in the front output shaft 31; The forward oil inlet sleeve 14 is disposed at the rear end of the input shaft 4 and connected to the reverse forward control valve 50, and is used to input working oil into the forward working oil passage 59, thereby controlling the forward piston 5 to move between the first position and the second position; The reverse oil inlet cover 41 is disposed at the rear end of the reverse shaft 42 and connected to the reverse control valve 50 for inputting working oil into the reverse working oil circuit 60, thereby controlling the reverse piston 48 to move between the first position and the second position; The output shaft oil inlet seat 32 is arranged at the front end of the front output shaft 31, and is used to input working oil to the first front output shaft working oil circuit 61, so as to control the output shaft piston 29 and the guide piston 25 to move between their first position and the second position respectively. When the output shaft piston 29 moves to the second position, the second front output shaft working oil circuit 62 is connected, so that the working oil enters the reverse control valve 50 through the second front output shaft working oil circuit 62.

[0091] Since the oil pump 16 is connected to the input shaft 4 via the oil pump coupling 15 , when the diesel engine drives the input shaft 4 to rotate, the oil pump 16 can be driven to work.

[0092] Specifically, after the diesel engine is started, the input shaft 4 rotates driven by the diesel engine, driving the oil pump 16 to start working. The oil pump 16 allows the working oil to act on the output shaft clutch 56 through the first front output shaft working oil circuit 61, and when the output shaft piston 29 is pushed to move to the positioning ring 27, the output shaft clutch 56 is engaged and the second front output shaft working oil circuit 62 is connected. The working oil enters the reverse and forward control valve 50 through the second front output shaft working oil circuit 62. The reverse and forward control valve 50 working oil circuits are connected, and reverse and forward control operations can be performed.

[0093] refer to Figure 2-5 In one embodiment, the gearbox further comprises: A box assembly 45, wherein the front end of the input shaft 4 is supported on the box assembly 45 through a first rolling bearing 3 sleeved on the input shaft transmission gear 2, and the rear end of the input shaft 4 is tightly mounted on the input shaft seat 13, and the rear end of the input shaft 4 is supported on the box assembly 45 through a second rolling bearing 10 and a first thrust ball bearing 12 sleeved on the input shaft seat 13, and the first thrust ball bearing 12 bears the axial force of the input shaft 4 through a first rolling bearing seat 11 tightly connected to the box assembly 45; In some feasible embodiments, the front end of the reverse shaft 42 is supported on the box assembly 45 through a third rolling bearing 34 mounted on the reverse transmission gear 35, and the rear end of the reverse shaft 42 is tightly mounted on the reverse shaft seat 43. The rear end of the reverse shaft 42 is supported on the box assembly 45 through a fourth rolling bearing 39 and a second thrust ball bearing 40 mounted on the reverse shaft seat 44, and the second thrust ball bearing 40 bears the axial force of the reverse shaft 42 through a second rolling bearing seat 44 tightly connected to the box assembly 45.

[0094] In the prior art, gearboxes generally use multiple sliding bearings to support the input shaft and the reverse shaft respectively, resulting in a large size and heavy weight of the gearbox. However, rolling bearings are not strong enough and have poor force-bearing capacity, so they cannot be used to support the input shaft and the reverse shaft in gearboxes used in high-power scenarios. If they are barely used, the bearing life will be too short.

[0095] In the embodiment of the present invention, the input shaft 4 and the reverse shaft 42 are supported by using two rolling bearings and one thrust bearing, preferably a thrust ball bearing. The axial force of the gear and the radial force of the gear are decomposed and borne by different bearings. The two rolling bearings bear the radial force of the gear, and the one thrust bearing bears the axial force of the gear. This solves the technical problems of poor force bearing capacity and short life of rolling bearings, so that rolling bearings can be used for the input shaft and the reverse shaft, thereby reducing the weight of the gear box. It also has a simple structure and is reliable to use.

[0096] In one embodiment, the gearbox further comprises: The front end of the front output shaft 31 is supported on the box assembly 45 through the fifth bearing 33, the output shaft bearing 21 is sleeved on the rear end of the front output shaft 31, and the rear output shaft 20 is sleeved on the output shaft bearing 21; The rear output shaft 20 is supported on the box assembly 45 via a sixth bearing 17 and a seventh bearing 18 .

[0097] refer to Figure 1 , 9 10. In one embodiment, the box assembly 45 includes: A front box 49, a rear box 51 and a lower box 52; The front box body 49 and the rear box body 51 are assembled into an upper box body, and a joint edge is provided at the matching position of the front box body 49 and the rear box body 51; The surface of the upper box body and / or the lower box body 52 is provided with reinforcing ribs; the upper box body and the lower box body 52 are fixed by flange cooperation.

[0098] The housing assembly of the embodiment of the present invention is assembled into a complete housing by assembling a front housing, a rear housing, and a lower housing, which improves the convenience of assembly and disassembly of the gear box and facilitates mass production. The rigidity of the housing is improved by using joining edges, reinforcing ribs, and fixing the upper and lower housings with flanges.

[0099] The main transmission relationship of the gearbox in the embodiment of the present invention is: the input coupling 1 is connected to the input shaft 4, the input shaft transmission gear 2 is connected to the forward driving gear 9 through the forward clutch 54, the forward driving gear 9 can be meshed with the driven gear 30 fixed on the front output shaft 31, the input shaft transmission gear 2 can also be meshed with the reverse transmission gear 35, the reverse transmission gear 35 is connected to the reverse driving gear 38 through the reverse clutch 55, the reverse driving gear 38 is meshed with the driven gear 30, the front output shaft 31 is connected to the rear output shaft 20 through the output shaft clutch 56, and the rear output shaft 20 is connected to the output coupling 19.

[0100] The working mode of the gearbox of the embodiment of the present invention is as follows: The working mode of the forward clutch 54 of the embodiment of the present invention is as follows: when the reverse forward control valve 50 issues a forward command, the hydraulic system works, and the working oil pushes the forward piston 5 from the forward working oil circuit 59, thereby pushing the first outer friction plate 7 and the first inner friction plate 8 to be pressed tightly, and the input shaft transmission gear 2 and the forward driving gear 9 are combined; when the reverse forward control valve 50 instructs to stop, the forward piston 5 retreats under the action of the forward spring 6, the first outer friction plate 7 and the first inner friction plate 8 are released, and the input shaft transmission gear 2 and the forward driving gear 9 are disengaged.

[0101] The working mode of the reverse clutch 55 of the embodiment of the present invention is as follows: when the reverse control valve 50 issues a reverse command, the hydraulic system works, and the working oil from the reverse working oil circuit 60 pushes the reverse piston 48, thereby pushing the second outer friction plate 36 and the second inner friction plate 37 to be pressed, and the reverse transmission gear 35 is combined with the reverse driving gear 38; when the reverse control valve 50 instructs to stop, the reverse piston 48 retreats under the action of the reverse spring 47, the second outer friction plate 36 and the second inner friction plate 37 are released, and the reverse transmission gear 35 is disengaged from the reverse driving gear 38.

[0102] The working mode of the output shaft clutch of the embodiment of the present invention is as follows: the diesel engine is started, driving the input shaft 4 to rotate, and then driving the oil pump 16 to work, so that the working oil pushes the guide piston 25 and the output shaft piston 29 through the first front output shaft working oil passage 61, and the guide piston 25 reaches the preset position first, and the guide piston 25 pushes the hickey disc 24 to move, and the hickey disc 24 moves under the guiding action of the guide disc 22 until it meshes with the hickey disc seat 23. At this time, the inner teeth of the rear output shaft correspond to the outer teeth of the output shaft piston. Under the pressure of the working oil, the output shaft piston 29 continues to move until it reaches the preset position defined by the positioning ring 27, and the outer teeth of the output shaft piston mesh with the inner teeth of the driven gear and the inner teeth of the rear output shaft at the same time, and the front output shaft 31 is combined with the rear output shaft 20; when the hydraulic system stops working, under the action of the output shaft spring 28, the output shaft piston 29 retreats, and under the action of the guide spring 53, the guide piston 25 retreats, driving the hickey disc 24 to retreat, and at this time, the front output shaft 31 is disengaged from the rear output shaft 20.

[0103] When the diesel engine is started, the oil pump 16 starts working, and the working oil drives the output shaft clutch 56 to combine the front output shaft 31 with the rear output shaft 20; the diesel engine flywheel is connected to the input shaft 4 through the input coupling 1, and the diesel engine power is input into the gearbox. At the same time, the working oil enters the reverse and forward control valve 50, and the reverse and forward control valve 50 can reverse or forward the gearbox; the rear output shaft 20 of the gearbox is connected to the load machinery, such as a propeller, so that the diesel engine drives the load machinery to work through the gearbox.

[0104] The diesel engine is turned off, the oil pump 16 stops working, the output shaft clutch 56 disengages the front output shaft 31 from the rear output shaft 20, the rear output shaft 20 of the gearbox is connected to the motor shaft, the motor starts, and the motor shaft drives the rear output shaft of the gearbox. The output shaft 20 rotates, and then connects to a load machine, such as a propeller, through the rear output shaft 20 of the gear box. Thus, the motor drives the load machine to work, the rear output shaft idles, and the gear box does not work, and will not be damaged due to lack of working oil lubrication caused by the oil pump 16 stopping working.

[0105] In a third aspect, an embodiment of the present invention further provides a vehicle, the vehicle comprising the gearbox described above. The vehicle is, for example, a ship.

[0106] The above is an explanation of the embodiments of the present invention. However, the present invention is not limited to the above embodiments. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. An output shaft clutch, characterized in that: The output shaft clutch (56) is used to control the transmission engagement or disengagement between the front output shaft (31) and the rear output shaft (20) of the gear box; It includes: An output shaft piston (29), wherein the output shaft piston (29) is capable of sliding axially along the front output shaft (31), and the output shaft piston (29) has a first position and a second position; When the output shaft piston (29) is located at the first position, the output shaft clutch (56) is disengaged, and the front output shaft (31) and the rear output shaft (20) are in a disengaged state; when the output shaft piston (29) is located at the second position, the output shaft clutch (56) is engaged, and the front output shaft (31) and the rear output shaft (20) are in an engaged state.

2. The output shaft clutch according to claim 1, characterized in that: The output shaft piston (29) has output shaft piston external teeth, and the output shaft piston external teeth are used to mesh with the internal teeth of the driven gear (30); The driven gear (30) is mounted on the front output shaft (31) and is used to receive power transmitted by a transmission mechanism of a gear box; The rear output shaft (20) has rear output shaft internal teeth, and the rear output shaft internal teeth are used to mesh with the output shaft piston external teeth; When the output shaft piston (29) is located at the first position, the external teeth of the output shaft piston mesh with the internal teeth of the driven gear, and the external teeth of the output shaft piston are disengaged from the internal teeth of the rear output shaft; When the output shaft piston (29) is located at the second position, the external teeth of the output shaft piston are simultaneously meshed with the internal teeth of the driven gear and the internal teeth of the rear output shaft.

3. The output shaft clutch according to claim 2, characterized in that: Also includes: An output shaft spring seat (26) disposed on the front output shaft (31); an output shaft spring (28), which is arranged between the output shaft spring seat (26) and the output shaft piston (29); The output shaft piston (29) is located at a first position under the limiting action of the output shaft spring (28); when the hydraulic system is working, the output shaft piston (29) compresses the output shaft spring (28) under the action of the hydraulic system and reaches a second position.

4. The output shaft clutch according to any one of claims 1 to 3, characterized in that: Also includes: A guide mechanism is provided between the driven gear (30) and the rear output shaft (20), and the guide mechanism is used for guiding when the front output shaft (31) is combined with the rear output shaft (20).

5. The output shaft clutch according to claim 4, characterized in that: The guiding mechanism comprises: A guide piston (25), wherein the guide piston (25) is capable of sliding axially along the front output shaft (31), and the guide piston (25) has a first position and a second position; A rat-tooth disc (24), the rat-tooth disc (24) being connected to the guide piston (25), the rat-tooth disc (24) having rat-tooth disc teeth; A rat-tooth disc seat (23), the rat-tooth disc seat (23) being arranged on the rear output shaft (20), the rat-tooth disc seat (23) having rat-tooth disc seat teeth, and the rat-tooth disc seat teeth being used to mesh with the rat-tooth disc teeth; When the guide piston (25) is located at a first position, the rat-tooth disc seat teeth are disengaged from the rat-tooth disc teeth; when the guide piston (25) is located at a second position, the rat-tooth disc seat teeth are meshed with the rat-tooth disc teeth.

6. The output shaft clutch according to claim 5, characterized in that: The guiding mechanism also includes: A guide plate (22), the guide plate (22) being arranged on the front output shaft (31), the guide plate (22) having guide plate external teeth; The rat-tooth disk (24) has rat-tooth disk inner teeth, the rat-tooth disk inner teeth meshing with the guide disk outer teeth, and are used to guide the sliding of the rat-tooth disk (24); And / or, the guide plate (22) has guide plate internal teeth, the front output shaft (31) has front output shaft external teeth, and the guide plate internal teeth mesh with the front output shaft external teeth.

7. The output shaft clutch according to claim 6, characterized in that: The guiding mechanism also includes: a guide spring (53), the guide spring (53) being arranged between the guide piston (25) and the guide plate (22); The guide piston (25) is located at a first position under the limiting action of the guide spring (53); when the hydraulic system is working, the guide piston (25) compresses the guide spring (53) under the action of the hydraulic system and reaches a second position; And / or, the guide piston (25) has a front end and a rear end, and when the guide piston (25) is in the first position, the front end of the guide piston abuts against the output shaft spring seat (26), and the rear end of the guide piston is provided with a receiving space; And / or, the main body of the guide spring (53) is at least partially disposed in the accommodation space at the rear end of the guide piston; And / or, the Hirth disk (24) is mounted on the rear end surface of the guide piston.

8. A gearbox, comprising an input shaft (4) and an output shaft, characterized in that: The output shaft comprises a front output shaft (31) and a rear output shaft (20); The gearbox further comprises an output shaft clutch (56) as claimed in any one of claims 1 to 7, wherein the output shaft clutch (56) is used to control the coupling transmission or disengagement between the front output shaft (31) and the rear output shaft (20); When only the diesel engine provides power, the front output shaft (31) and the rear output shaft (20) are connected to each other through the output shaft clutch (56) for transmission, and the power is output to the outside through the input shaft (4), other transmission components in the gear box, and the front output shaft (31) and the rear output shaft (20); When only the motor provides power, the output shaft clutch (56) is disengaged, the front output shaft (31) and the rear output shaft (20) are disengaged, and only the rear output shaft (20) in the gear box is connected to the motor shaft; When the diesel engine and the motor provide power simultaneously, the front output shaft (31) and the rear output shaft (20) are coupled for transmission via the output shaft clutch (56), and the rear output shaft (20) in the gear box is connected to the motor shaft.

9. The gearbox according to claim 8, characterized in that The front output shaft (31) and the rear output shaft (20) are coaxially arranged; And / or, the front output shaft (31) and the rear output shaft (20) are supported by the same bearing.

10. The gearbox according to claim 8, characterized in that The front output shaft (31) and the rear output shaft (20) are supported by output shaft bearings (21); And / or, the output shaft bearing (21) is sleeved on the front output shaft (31), and the output shaft bearing (21) is embedded in the rear output shaft (20); And / or, the output shaft bearing (21) is sleeved on the rear output shaft (20), and the output shaft bearing (21) is embedded in the front output shaft (31).

11. The gearbox according to claim 8, characterized in that Also includes: An input coupling (1), the input coupling (1) being connected to the input shaft (4) and used for driving the input shaft (4) to rotate; An input shaft transmission gear (2) is provided on the input shaft (4), and a driving gear (9) is provided in an empty sleeve on the input shaft (4); And / or, the onboard driving gear (9) is capable of meshing with the driven gear (30) to drive the front output shaft (31) to rotate; And / or, the rear output shaft (20) can be transmission-connected to the motor shaft; And / or, the motor is a DC motor.

12. The gearbox according to claim 11, characterized in that Also includes hydraulic system: The hydraulic system comprises a reverse and forward control valve (50) and a working oil circuit; The forward and reverse control valve (50) is used to control the engagement and disengagement of the forward clutch (54) and the reverse clutch (55); The working oil circuit is used to transport working oil, and comprises a forward working oil circuit (59) arranged in the input shaft (4), a reverse working oil circuit (60) arranged in the reverse shaft (42), and a first front output shaft working oil circuit (61) and a second front output shaft working oil circuit (62) arranged in the front output shaft (31); The oil pump (16) can work under the drive of the input shaft (4) and is used to deliver working oil to the output shaft clutch (56) and the reverse control valve (50).

13. The gearbox according to claim 12, characterized in that The hydraulic system further comprises an oil pump (16), a forward oil inlet sleeve (14), a reverse oil inlet cover (41) and an output shaft oil inlet seat (32); The forward oil inlet sleeve (14) is connected to the reverse forward control valve (50) and is used to input working oil into the forward working oil circuit (59); The reverse oil inlet cover (41) is connected to the reverse and forward control valve (50) and is used to input working oil into the reverse working oil circuit (60); The output shaft oil inlet seat (32) is connected to the oil pump (16) and is used to input working oil into the first front output shaft working oil circuit (61).

14. The gearbox according to claim 8, characterized in that Also included is a housing assembly (45): The box assembly (45) comprises a front box (49), a rear box (51) and a lower box (52), wherein the front box (49) and the rear box (51) are assembled into an upper box; And / or, the upper box body is provided with a joint edge at the matching position between the front box body (49) and the rear box body (51); And / or, the surface of the lower box (52) is provided with reinforcing ribs; And / or, the upper box body and the lower box body (52) are fixed by flange cooperation.

15. A vehicle, characterized in that: It comprises a gearbox, and the gearbox is as described in any one of claims 8-14; the carrier is a ship.

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