Power assembly with combined oil injection pipe, oil injection pipe and vehicle

Abstract

The utility model provides a power assembly with a combined oil injection pipe, the oil injection pipe and a vehicle. The power assembly comprises a shell and an oil spraying pipe, the shell is used for containing a speed reducer of the power assembly and fixing the oil spraying pipe, the oil spraying pipe comprises an oil conveying pipe and a combined nozzle which are integrally formed, the oil conveying pipe comprises an oil inlet pipe and a plurality of oil outlet pipes, and the oil outlet pipes are used for receiving cooling liquid through the oil inlet pipe. Each oil outlet pipe is used for outputting cooling liquid to at least lubricate a gear or a bearing of the speed reducer, one end of the nozzle is used for being fixedly connected with the oil outlet pipes in the multiple oil outlet pipes and used for receiving the cooling liquid output by the oil outlet pipes, and an opening in the other end of the nozzle is used for outputting the cooling liquid; the aperture of the opening at one end of the nozzle is larger than that of the oil outlet pipe and that of the opening at the other end of the nozzle. The oil spraying pipe of the power assembly integrates the multiple oil outlet pipes, the structure of the oil spraying pipe can be simplified, and the manufacturing difficulty of the oil spraying pipe can be lowered.

Description

Technical Field

[0001] The present application relates to the technical field of powertrain, and in particular to a powertrain with a combined fuel injection pipe, a fuel injection pipe with a combined nozzle, and a vehicle. Background Art

[0002] One of the keys to ensure the normal and stable operation of the powertrain is to transport coolant through the oil pipe in the oil injection pipe to lubricate or dissipate heat for the internal functional structure of the powertrain. Among them, the gears and bearings used for transmission in the powertrain are arranged at different positions in the housing, that is, the layout direction and position of each lubrication position in the powertrain are different.

[0003] However, it is difficult to ensure the accuracy of the fuel injection pipe installed in the powertrain in delivering coolant to multiple locations to be lubricated at the same time, which increases the structural complexity and preparation difficulty of the fuel injection pipe. Utility Model Content

[0004] The present application provides a powertrain with a combined fuel injection pipe. By optimizing the structural design of the fuel delivery pipe in the fuel injection pipe carried by the powertrain, the fuel injection pipe can ensure that the coolant is delivered to multiple locations to be lubricated at the same time, and the overall structure of the fuel injection pipe can be simplified and the difficulty of preparing the fuel injection pipe can be reduced. The present application also provides a fuel injection pipe and a vehicle with a combined nozzle. The present application specifically includes the following technical solutions:

[0005] In a first aspect, the present application provides a powertrain with a combined fuel injection pipe, the powertrain comprising a shell and a combined fuel injection pipe, the shell being used to accommodate a reducer of the powertrain and to fix a fuel injection pipe, a fuel injection pipe comprising an integrally formed fuel delivery pipe and a combined nozzle, a fuel delivery pipe comprising an fuel inlet pipe and multiple fuel outlet pipes, the multiple fuel outlet pipes being used to receive coolant through an fuel inlet pipe, each fuel outlet pipe being used to output coolant to lubricate at least one of a gear or a bearing of the reducer, one end of a nozzle being used to fixedly connect to an fuel outlet pipe among the multiple fuel outlet pipes and to receive coolant output by an fuel outlet pipe, an opening at the other end of a nozzle being used to output coolant, wherein the aperture of the opening at one end of a nozzle is larger than the aperture of an fuel outlet pipe and larger than the aperture of the opening at the other end of a nozzle.

[0006] The reducer of the powertrain of the present application is housed in a housing, and the housing can protect the functional structural parts of the reducer to prevent dust, foreign matter and other impurities in the external environment from invading the reducer and reducing the working performance and life of the reducer. The powertrain is equipped with a fuel injection pipe, which can transport coolant to lubricate the transmission structure in the powertrain to improve the working performance and life of the transmission mechanism. A fuel injection pipe is fixedly connected to the housing, and the housing can form a supporting effect on a fuel injection pipe, ensuring that a fuel injection pipe can stably and continuously transport coolant to the position to be lubricated in the powertrain, avoiding undesirable phenomena such as shaking and displacement of a fuel injection pipe during the operation of the powertrain. That is, the support and fixing effect of a fuel injection pipe formed by the housing can improve the precision and accuracy of a fuel injection pipe in transporting coolant.

[0007] The multiple oil outlet pipes of an oil injection pipe of the powertrain of the present application respectively correspond to the positions to be lubricated at different positions of the transmission structure in the powertrain, so that coolant can be transported to different positions to be lubricated for lubrication at the same time. For example, coolant can be transported to gears and bearings at different positions of the reducer for lubrication through multiple oil outlet pipes, which can improve the lubrication efficiency of an oil injection pipe. An oil injection pipe transports coolant to multiple oil outlet pipes at the same time through an oil inlet pipe, thereby improving the efficiency of an oil inlet pipe in transporting coolant to multiple oil outlet pipes. At the same time, multiple oil outlet pipes are simultaneously connected to the outer peripheral wall of an oil inlet pipe, and an oil inlet pipe and multiple oil outlet pipes are prepared in an integrated molding manner, which simplifies the structural design of an oil delivery pipe and reduces the difficulty of preparing an oil delivery pipe to improve the preparation efficiency of an oil injection pipe. A nozzle of an oil injection pipe corresponds to an oil outlet pipe, and the coolant output by an oil outlet pipe is transported to a gear or a bearing periphery of the reducer through a nozzle for lubrication. Along the direction of coolant flow, since the aperture of the opening at the other end of a nozzle is smaller than the aperture of the opening at one end of a nozzle, the pressure of the coolant at the other end of a nozzle is greater than the pressure of the coolant at one end of a nozzle, thereby achieving the effect of increasing the output coolant pressure. When an oil outlet pipe is far away from its corresponding position to be lubricated or the viscosity of the coolant is too high at low temperature, the position to be lubricated, such as a gear or a bearing in a reducer, can increase the delivery distance and output flow rate of the coolant delivered by an oil outlet pipe by increasing the pressure of the coolant output by a nozzle, thereby ensuring that an oil outlet pipe can accurately deliver coolant to the position to be lubricated and that an oil outlet pipe can deliver enough coolant flow to the position to be lubricated for lubrication. At the same time, the split design of an oil delivery pipe and a nozzle of an oil injection pipe can ensure the precision and accuracy of the coolant delivery by an oil injection pipe, simplify the structure of an oil injection pipe, reduce the difficulty and cost of preparing an oil injection pipe, and improve the preparation efficiency of an oil injection pipe.

[0008] In one implementation, an oil pipeline is an injection molded part.

[0009] Accordingly, an oil pipeline is prepared by injection molding, so that the oil pipeline is formed in one piece, which reduces the difficulty of preparing an oil pipeline and improves the preparation efficiency of an oil pipeline, thereby improving the overall preparation efficiency of the powertrain. The material of the injection molded part is usually rubber or plastic with a relatively light weight. Therefore, preparing an oil pipeline by injection molding can reduce the weight of an oil pipeline, thereby reducing the overall weight of the powertrain to meet the lightweight design requirements of the powertrain. That is, an oil pipeline is formed in one piece by injection molding, so that the oil pipeline can transport coolant to multiple locations to be lubricated while also taking into account the lightweight design requirements of the powertrain.

[0010] In one implementation, along the direction of coolant flow, the axis of a nozzle coincides with the axis of an oil outlet pipe, wherein an oil outlet pipe is connected to one end of a nozzle by welding.

[0011] Accordingly, one end of a nozzle and an oil outlet pipe are fixed by welding, and no additional structure is needed between an oil outlet pipe and a nozzle to achieve the fixation between the two, thereby further simplifying the structural design of a nozzle and an oil outlet pipe. In addition, a nozzle and an oil outlet pipe are fixed by welding, which simplifies the structure of a nozzle and an oil outlet pipe and improves the stability and reliability of the mutual fixation of a nozzle and an oil outlet pipe.

[0012] In one implementation, a nozzle includes a first annular protrusion, wherein the first annular protrusion is located at one end of the nozzle along the direction of coolant flow, and the first annular protrusion is welded and fixed to the end surface of an oil outlet pipe facing the nozzle, wherein the first annular protrusion is arranged around the periphery of an opening at one end of the nozzle, and along the radial direction of the oil outlet pipe, the inner diameter of the first annular protrusion is larger than the inner diameter of the oil outlet pipe, and the outer diameter of the first annular protrusion is smaller than the outer diameter of the oil outlet pipe.

[0013] Accordingly, along the direction of coolant flow, a first annular protrusion is protruded on the end face of a nozzle facing an oil outlet pipe, and extends toward an oil outlet pipe along the axial direction of a nozzle. A nozzle is welded to the end face of an oil outlet pipe through a first annular protrusion, which can improve the welding efficiency and accuracy of a nozzle and an oil outlet pipe. Among them, along the direction of coolant flow, the projection of a first annular protrusion on the end face of an oil outlet pipe is contained in the end face of an oil outlet pipe, so that a first annular protrusion can form a containment effect on the coolant at the connection position between an oil outlet pipe and a nozzle, thereby improving the efficiency and effect of conveying coolant from an oil outlet pipe to a nozzle.

[0014] In one implementation, an oil outlet pipe includes a second annular protrusion, and along the direction of coolant flow, the second annular protrusion is located on the end surface of the oil outlet pipe facing a nozzle, wherein, along the radial direction of the oil outlet pipe, the inner diameter of the second annular protrusion is greater than or equal to the aperture of the oil outlet pipe, the outer diameter of the second annular protrusion is less than or equal to the inner diameter of the first annular protrusion, and along the direction of coolant flow, the extension length of the second annular protrusion is less than or equal to the extension length of the first annular protrusion.

[0015] Correspondingly, a second annular protrusion is provided on the end face of an oil outlet pipe facing a nozzle along the direction of coolant flow, and the second annular protrusion is located inside the first annular protrusion, and the second annular protrusion at least partially overlaps with the first annular protrusion in the direction of coolant flow. Due to the excess solder that may be generated when a first annular protrusion is welded to an oil outlet pipe, a second annular protrusion is provided inside the first annular protrusion, that is, a second annular protrusion is closer to the axis of an oil outlet pipe than a first annular protrusion, so that the second annular protrusion can block and contain the possible excess solder, thereby avoiding the excess solder that may be generated during welding from clogging an oil outlet pipe or a nozzle. The second annular protrusion of an oil outlet pipe cooperates with the first annular protrusion of a nozzle, which can improve the connection effect between a nozzle and an oil outlet pipe while ensuring the welding reliability of a nozzle and an oil outlet pipe, thereby improving the delivery efficiency and reliability of the coolant. In addition, by providing a second annular protrusion, a first annular protrusion and an oil outlet pipe can be positioned when welded, thereby improving the alignment effect of a nozzle and an oil outlet pipe, thereby further improving the accuracy and efficiency of an oil injection pipe in delivering coolant to the position to be lubricated.

[0016] In one implementation, an oil outlet pipe includes another second annular protrusion, and along the radial direction of the oil outlet pipe, the other second annular protrusion is arranged around the periphery of the second annular protrusion, wherein, along the radial direction of the oil outlet pipe, the inner diameter of the other second annular protrusion is greater than or equal to the outer diameter of the first annular protrusion, and along the direction of coolant flow, the extension length of the other second annular protrusion is less than or equal to the extension length of the first annular protrusion and greater than the extension length of the second annular protrusion.

[0017] Correspondingly, another second annular protrusion is located at the periphery of a second annular protrusion, and a second annular protrusion and another second annular protrusion are arranged at intervals along the radial direction of an oil outlet pipe to form an annular groove structure between a second annular protrusion and another second annular protrusion. The groove structure formed between the two second annular protrusions can accommodate a first annular protrusion of a nozzle to form a first annular protrusion avoidance effect, thereby reducing the structural dimensions of an oil outlet pipe and a nozzle along the direction of coolant flow, and realizing a miniaturized design of an oil injection pipe. Along the direction of coolant flow, the extension length of a first annular protrusion of a nozzle is greater than the extension length of each second annular protrusion, so that after a first annular protrusion extends into the groove structure, it can abut against the end face of an oil outlet pipe facing a nozzle to be fixed by welding.

[0018] In one implementation, along the radial direction of an oil outlet pipe, the interval between one second annular protrusion and another second annular protrusion is greater than the thickness of a first annular protrusion, wherein the thickness of one second annular protrusion is less than or equal to the thickness of another second annular protrusion.

[0019] Accordingly, along the radial direction of an oil outlet pipe, a gap is formed between a first annular protrusion and each second annular protrusion, so that a first annular protrusion and two second annular protrusions cooperate with each other, and the gaps are used to accommodate the excess solder that may be generated when welding a nozzle and an oil outlet pipe, thereby improving the effect of accommodating possible excess solder and further improving the connection effect between a nozzle and an oil outlet pipe. At the same time, among the two second annular protrusions, the second annular protrusion that is closer to the axis of an oil outlet pipe is thinner than the other second annular protrusion, which can reduce the overall weight of an oil injection pipe and achieve the effect of miniaturized design of an oil injection pipe.

[0020] In one implementation, a nozzle also includes another first annular protrusion, which is located on a side of a nozzle away from a first annular protrusion along the direction of coolant flow, wherein an outer diameter of the other first annular protrusion is smaller than an outer diameter of a first annular protrusion and smaller than or equal to an inner diameter of a first annular protrusion.

[0021] Correspondingly, along the direction of coolant flow, the aperture of the opening at the other end of a nozzle is smaller than the aperture of the opening at one end of a nozzle. At this time, the outer diameter of the other end of a nozzle is set to be smaller than the outer diameter of one end of a nozzle, so as to simplify the structural design of a nozzle and reduce the overall weight of a nozzle. It can be understood that since one end of a nozzle is welded to an oil outlet pipe, by reducing the weight of the other end of a nozzle, the welding stability and reliability of a nozzle and an oil outlet pipe can be improved, avoiding the undesirable phenomenon that the welding position between a nozzle and an oil outlet pipe may be broken due to the excessive weight of the other end of a nozzle.

[0022] In one implementation, a nozzle includes two connected sections along the direction of coolant flow, one section is used to receive coolant transported by an oil outlet pipe and transport it to another section, and the other section is used to output coolant, wherein, along the direction of coolant flow, the extension length of one section is greater than the extension length of the other section, the aperture of one section gradually decreases along the direction of coolant flow, and the aperture of the other section is less than or equal to the minimum aperture of one section.

[0023] Accordingly, along the direction of coolant flow, one section is closer to an oil outlet pipe than the other section, and the aperture of one section gradually decreases, so that after receiving the coolant output by an oil outlet pipe, one section gradually pressurizes the coolant. That is, one section gradually increases the pressure of the coolant by setting its aperture along the direction of coolant flow, thereby improving the flow stability and stability of the coolant in a nozzle. The aperture of the other section is less than or equal to the aperture of one section, and the aperture of the other section remains unchanged, so that the coolant with increased pressure can be stably and accurately delivered from the other section to the lubrication position, further improving the stability and accuracy of the coolant delivery of a nozzle. At the same time, along the direction of coolant flow, the extension lengths of one section and another section of a nozzle are set differently, which can improve the stability and accuracy of the coolant output of a nozzle while reducing the structural dimensions of a nozzle along the direction of coolant flow, so as to achieve the effect of a miniaturized design of a nozzle.

[0024] In one implementation, an oil injection pipe also includes another combined nozzle, one end of the other nozzle is used to fixedly connect another oil outlet pipe among the multiple oil outlet pipes and to receive coolant delivered by the other oil outlet pipe, and the opening at the other end of the other nozzle is used to deliver coolant to lubricate another gear or another bearing of the reducer, wherein the other end of the other nozzle is flat-mouthed, and along the direction of coolant flow, the length dimension of the opening at the other end of the other nozzle is greater than the aperture of the other oil outlet pipe, and the width dimension of the opening at the other end of the other nozzle is smaller than the aperture of the other oil outlet pipe.

[0025] Correspondingly, another nozzle is also provided at the oil outlet end of another oil outlet pipe of the multiple oil outlet pipes, and the opening of the other end of the other nozzle facing the position to be lubricated is configured as a flat mouth shape to change the output shape of the coolant output by the other nozzle. It can be understood that by setting the opening of the other end of the other nozzle to be flat mouth shape, the coolant beam output by the other nozzle is squeezed in the length direction of the opening of the other end of the other nozzle, so as to achieve the diffusion of the spray coolant beam and expand the coverage range of the tooth surface. That is, the shape of the coolant output from the other nozzle is approximately linear or rectangular, so that the shape of the coolant output by the other nozzle can be matched and adapted to the shape of the position to be lubricated, so as to increase the coverage area of ​​the coolant output by the other nozzle. By setting the opening of the other end of the other nozzle to be flat mouth shape, the efficiency of a spray pipe in conveying coolant to lubricate the position to be lubricated can be further improved, and the loss of coolant can be reduced to save the cost of the powertrain. At the same time, the split design of an oil delivery pipe and another nozzle of an injection pipe can not only ensure the coverage area of ​​the coolant transported by the injection pipe, but also simplify the structure of the injection pipe, reduce the difficulty and cost of preparing the injection pipe, and improve the preparation efficiency of the injection pipe.

[0026] In one implementation, along the direction of coolant flow, the center line of another nozzle coincides with the axis of another oil outlet pipe, wherein the other oil outlet pipe is connected to one end of the other nozzle by welding.

[0027] Accordingly, one end of the other nozzle and the other oil outlet pipe are fixed by welding, and there is no need to design an additional structure between the other oil outlet pipe and the other nozzle to achieve the fixation between the two, thereby further simplifying the structural design of the other nozzle and the other oil outlet pipe. In addition, the other nozzle and the other oil outlet pipe are fixed by welding, which simplifies the structure of the other nozzle and the other oil outlet pipe and improves the stability and reliability of the fixation between the other nozzle and the other oil outlet pipe.

[0028] In one implementation, the opening of the other end of the other nozzle faces the other gear along the direction of coolant flow, wherein the length direction of the opening of the other end of the other nozzle is parallel to the axial direction of the other gear along the direction of coolant flow.

[0029] Accordingly, since the length direction of the meshing surface of the other gear and the other gear is parallel to the axial direction of the other gear, the length direction of the opening at the other end of the other nozzle is set to be parallel to the length direction of the meshing surface of the other gear and the other gear, so that the length direction of the linear or rectangular coolant output by the other nozzle is parallel to the length direction of the meshing surface. This can increase the coverage area of ​​the coolant output by the other nozzle on the position to be lubricated, and improve the lubrication efficiency of the coolant output by an injection pipe on the position to be lubricated, further improving the working performance and life of the powertrain.

[0030] In one implementation, an extension direction of an oil inlet pipe intersects with an extension direction of each oil outlet pipe, and an aperture of an oil inlet pipe is larger than an aperture of any of the multiple oil outlet pipes.

[0031] Accordingly, each oil outlet pipe is connected to the outer peripheral wall of an oil inlet pipe, and multiple oil outlet pipes can be arranged in the extension direction of an oil inlet pipe, and multiple oil outlet pipes are arranged at intervals along the extension direction of an oil inlet pipe, so that an oil inlet pipe can simultaneously deliver coolant to multiple oil outlet pipes, so as to improve the lubrication and heat dissipation efficiency of an oil injection pipe for the power assembly, and at the same time, it can also reduce the structural dimensions of an oil injection pipe along the extension direction of an oil inlet pipe, simplifying the internal structural design of the power assembly. Since an oil inlet pipe is used to deliver coolant to multiple oil outlet pipes at the same time, by setting the flow rate of coolant in an oil inlet pipe to be greater than the flow rate of coolant in each oil outlet pipe, it can be ensured that an oil injection pipe can deliver sufficient coolant to each position to be lubricated, so as to ensure the lubrication effect of each position to be lubricated, and further improve the working efficiency and life of the power assembly.

[0032] In one implementation, multiple oil outlet pipes are spaced apart from each other along the direction of coolant flow in an oil inlet pipe, wherein the interval between any two adjacent oil outlet pipes among the multiple oil outlet pipes is greater than the aperture of any of the two oil outlet pipes, and the angle between the extension direction of each oil outlet pipe and the direction of coolant flow in an oil inlet pipe is less than or equal to 90°.

[0033] Accordingly, the extension direction of each oil outlet pipe is the same as the direction of coolant flow, which can avoid turbulence that may occur in an oil inlet pipe and affect the smooth flow of coolant, thereby improving the stability and efficiency of coolant delivery from an oil inlet pipe to each oil outlet pipe.

[0034] In one implementation, the shell includes an oil delivery hole, which is used to deliver coolant to multiple oil outlet pipes through an oil inlet pipe, wherein an oil inlet pipe includes an oil inlet port, which is used to receive coolant delivered by an oil delivery hole, and along the direction of coolant flow in an oil inlet pipe, an oil inlet port is located on the same side of the opening of each oil outlet pipe connected to an oil inlet pipe.

[0035] Accordingly, along the extension direction of an oil inlet pipe, an oil inlet port is opened at one end of an oil inlet pipe, so that the coolant delivered from an oil delivery hole can be input into an oil inlet pipe from one end of an oil inlet pipe. Then, along the flow direction of the coolant in an oil inlet pipe, the coolant is sequentially delivered to each oil outlet pipe connected to the outer peripheral wall of an oil inlet pipe through an oil inlet pipe. It can be understood that receiving the coolant input from an oil delivery hole of the housing through an oil inlet port and sequentially delivering the coolant from one end of an oil inlet pipe to each oil outlet pipe can reduce the turning or diversion of the coolant in an oil inlet pipe, while improving the stability and stability of the coolant delivered from an oil inlet pipe to each oil outlet pipe, and can also ensure that the flow rate of the coolant delivered from an oil inlet pipe to each oil outlet pipe can meet the lubrication requirements of the lubricating position. At the same time, arranging multiple oil outlet pipes on the same side of an oil inlet port can further reduce the structural size of an oil injection pipe to further realize the miniaturization design of an oil injection pipe.

[0036] In one implementation, along the direction of coolant flow in each oil outlet pipe, the interval between each oil outlet pipe and a gear or a bearing of the reducer is less than or equal to 30 mm.

[0037] Accordingly, by setting the interval between each oil outlet pipe and a gear or a bearing of the reducer to be less than or equal to 30 mm, the coolant output by each oil outlet pipe can be reduced from being affected by other factors and may cause adverse phenomena such as conveying path deviation, thereby ensuring the accuracy and efficiency of a fuel injection pipe in conveying coolant to each position to be lubricated.

[0038] In the second aspect, the present application also provides an oil injection pipe with a combined nozzle, the oil injection pipe includes an integrally formed oil delivery pipe and a plurality of combined nozzles, the oil delivery pipe includes an oil inlet pipe and a plurality of oil outlet pipes, an oil inlet pipe is used to receive coolant and to deliver coolant to each oil outlet pipe, each oil outlet pipe is used to deliver coolant to a gear or a bearing of a reducer for lubrication, wherein one end of one of the multiple nozzles is used to be fixedly connected to one of the multiple oil outlet pipes by welding, and is used to receive coolant output by one oil outlet pipe, the aperture of the opening at one end of the one nozzle is larger than the aperture of the opening at the other end of the one nozzle, one end of another nozzle of the multiple nozzles is used to be fixedly connected to another oil outlet pipe of the multiple oil outlet pipes by welding, and is used to receive coolant output by another oil outlet pipe, the opening at the other end of the other nozzle is flat-mouthed, and one nozzle, another nozzle and the remaining one or the remaining multiple oil outlet pipes are respectively used to deliver coolant to a gear or a bearing at different positions in the reducer for lubrication.

[0039] The oil injection pipe provided in the present application delivers coolant to each oil outlet pipe through an oil inlet pipe, and delivers coolant to each lubricated position in the powertrain through each oil outlet pipe for lubrication, which can achieve the effect of integrating multiple oil outlet pipes into one oil injection pipe and delivering coolant to multiple lubricated positions at the same time, thereby improving the delivery efficiency of one oil injection pipe. At the same time, by setting each nozzle to be welded and fixed to an oil outlet pipe, while ensuring the accuracy of one oil injection pipe in delivering coolant to each lubricated position, it can also simplify the structural design of one oil injection pipe, reduce the difficulty of preparing one oil injection pipe, and improve the preparation efficiency of one oil injection pipe.

[0040] In a third aspect, the present application also provides a vehicle, comprising wheels and a powertrain provided by any of the above-mentioned implementations or a fuel injection pipe provided by any of the above-mentioned implementations, wherein the powertrain is used to drive the wheels.

[0041] The powertrain of the vehicle provided in the present application is connected to the wheels in a transmission manner, so that the power output by the powertrain is transmitted to the wheels, so as to achieve the effect of driving the wheels to rotate and then driving the vehicle to travel. The vehicle of the present application is equipped with a powertrain in any of the above-mentioned implementations, which can improve the working performance and life of the vehicle of the present application. Or, the vehicle of the present application is equipped with a fuel injection pipe in any of the above-mentioned implementations, which can improve the working efficiency and life of the vehicle. That is, because the powertrain in any of the above-mentioned implementations or the fuel injection pipe in any of the above-mentioned implementations is used, the vehicle of the present application has all the possible beneficial effects of the powertrain provided by any of the above-mentioned implementations or the fuel injection pipe provided by any of the above-mentioned implementations. BRIEF DESCRIPTION OF THE DRAWINGS

[0042] In order to more clearly illustrate the technical solution of the present application, the drawings required for use in the implementation manner will be briefly introduced below. Obviously, the drawings described below are only some implementation manners of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0043] Figure 1 A schematic diagram of a working scenario of a powertrain provided in an embodiment of the present application;

[0044] Figure 2 A schematic diagram of the planar structure of a powertrain provided in an embodiment of the present application;

[0045] Figure 3 A schematic diagram of the working principle of active lubrication of internal coolant of a powertrain provided in an embodiment of the present application;

[0046] Figure 4 This is a schematic diagram of the appearance structure of the powertrain provided in the embodiment of the present application with some structures hidden;

[0047] Figure 5 This is a schematic diagram of the appearance structure of the powertrain provided in the embodiment of the present application with some structures hidden;

[0048] Figure 6 A schematic diagram of the appearance structure of the fuel injection pipe of the power assembly provided in an embodiment of the present application;

[0049] Figure 7 A schematic diagram of the planar structure of the fuel injection pipe of the power assembly provided in an embodiment of the present application;

[0050] Figure 8 A schematic diagram of a partial appearance structure of a powertrain provided in an embodiment of the present application;

[0051] Fig. 9 This is a schematic diagram of the appearance structure of the powertrain provided in the embodiment of the present application with some structures hidden;

[0052] Fig.10 This is a schematic diagram of the appearance structure of the powertrain provided in the embodiment of the present application with some structures hidden;

[0053] Fig.11 A schematic diagram of the appearance structure of the fuel injection pipe of the power assembly provided in an embodiment of the present application;

[0054] Fig.12 A schematic diagram of the appearance structure of the fuel injection pipe of the power assembly provided in an embodiment of the present application;

[0055] Fig.13 A schematic diagram of a partial cross-sectional structure of an injection pipe of a powertrain provided in an embodiment of the present application;

[0056] Fig.14 A schematic diagram of a partial cross-sectional structure of an injection pipe of a powertrain provided in an embodiment of the present application;

[0057] Fig.15 A schematic diagram of the planar structure of a nozzle of a power assembly provided in an embodiment of the present application;

[0058] Fig.16 A schematic diagram of the planar structure of another nozzle of the power assembly provided in an embodiment of the present application;

[0059] Fig.17 A schematic diagram of the planar structure of another nozzle of the power assembly provided in an embodiment of the present application;

[0060] Fig.18 This is a schematic diagram of the appearance structure of the oil guide groove of the power assembly provided in an embodiment of the present application. DETAILED DESCRIPTION

[0061] The technical solutions in the embodiments of the present application will be described below in conjunction with the accompanying drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without making creative work belong to the scope of protection claimed in the present application.

[0062] The present application provides a powertrain with a combined fuel injection pipe, the powertrain comprising a shell and a combined fuel injection pipe, the shell being used to accommodate a reducer of the powertrain and to fix a fuel injection pipe, the fuel injection pipe comprising an integrally formed fuel delivery pipe and a combined nozzle, the fuel delivery pipe comprising an fuel inlet pipe and a plurality of fuel outlet pipes, the plurality of fuel outlet pipes being used to receive coolant through an fuel inlet pipe, each fuel outlet pipe being used to output coolant to lubricate at least one of a gear or a bearing of the reducer, one end of a nozzle being used to fixedly connect to an fuel outlet pipe among the plurality of fuel outlet pipes and to receive coolant output by an fuel outlet pipe, the opening at the other end of a nozzle being used to output coolant, wherein the aperture of the opening at one end of a nozzle is larger than the aperture of an fuel outlet pipe and larger than the aperture of the opening at the other end of a nozzle. The combined fuel injection pipe carried by the powertrain of the present application can simultaneously deliver coolant to multiple locations to be lubricated and can ensure the delivery accuracy of the coolant. It can also simplify the overall structure of the fuel injection pipe and reduce the difficulty of preparing the fuel injection pipe through targeted and optimized structural design, thereby improving the preparation efficiency of the powertrain.

[0063] The present application provides an oil injection pipe with a combined nozzle, the oil injection pipe comprising an integrally formed oil delivery pipe and a plurality of combined nozzles, the oil delivery pipe comprising an oil inlet pipe and a plurality of oil outlet pipes, the oil inlet pipe being used to receive coolant and to deliver coolant to each oil outlet pipe, each oil outlet pipe being used to deliver coolant to a gear or a bearing of a reducer for lubrication, wherein one end of one of the multiple nozzles is used to be fixedly connected to one of the multiple oil outlet pipes by welding and to receive coolant output by one oil outlet pipe, the aperture of an opening at one end of one nozzle is larger than the aperture of an opening at the other end of one nozzle, one end of another nozzle of the multiple nozzles is used to be fixedly connected to another oil outlet pipe of the multiple oil outlet pipes by welding and to receive coolant output by another oil outlet pipe, the opening at the other end of the other nozzle is flat-mouthed, and one nozzle, another nozzle and the remaining one or the remaining multiple oil outlet pipes are respectively used to deliver coolant to a gear or a bearing at different positions in the reducer for lubrication. The fuel injection pipe of the present application integrates multiple oil outlet pipes to simultaneously deliver coolant to multiple locations to be lubricated, thereby improving the delivery efficiency of a fuel injection pipe. At the same time, it can simplify the structural design of a fuel injection pipe and reduce the difficulty of preparing a fuel injection pipe to improve the preparation efficiency of a fuel injection pipe.

[0064] The present application provides a vehicle, the vehicle comprising wheels and a powertrain provided by any of the above implementations or a fuel injection pipe provided by any of the above implementations, the powertrain being used to drive the wheels. The vehicle of the present application is equipped with a powertrain provided by any of the above implementations or a fuel injection pipe provided by any of the above implementations, which can improve the working efficiency and life of the vehicle of the present application.

[0065] The present application provides a vehicle, the vehicle comprising wheels, a power battery and a power assembly, Figure 1 The powertrain of the present application is shown as powertrain 1000. The power battery is electrically connected to each functional structural component inside the vehicle, and the power battery can provide power for each functional structural component inside the vehicle to operate normally. The powertrain 1000 is used to receive the electrical energy provided by the power battery and to provide power to drive the wheels of the vehicle.

[0066] The wheels are rotatably connected to the body of the vehicle, and each wheel rotates to drive the frame of the vehicle to travel. The powertrain 1000 is fixedly connected to the body of the vehicle and is drivingly connected to the wheels of the vehicle. Exemplarily, the power battery supplies power to the powertrain 1000, and the powertrain 1000 receives electrical energy and outputs power to the wheel ends to drive the wheels to rotate. It can be understood that the powertrain 1000 of the vehicle is connected to the wheels through a speed reducer, so that the power output of the motor in the powertrain 1000 is transmitted to the speed reducer, and then transmitted to the wheels through the speed reducer, so as to achieve the effect of driving the wheels to rotate and then driving the vehicle to travel.

[0067] See also Figure 1 , Figure 1 Schematic diagram of the working scene of the powertrain 1000 provided in the embodiment of the present application. The powertrain 1000 includes a motor 1001, a reducer 1002 and a housing 1003, and at least one of the motor 1001 and the reducer 1002 is accommodated in the housing 1003. That is, the motor 1001 and the reducer 1002 may be but are not limited to being fully accommodated in the housing 1003, or only the motor 1001 may be but are not limited to being accommodated in the housing 1003, or only the reducer 1002 may be but are not limited to being accommodated in the housing 1003. Figure 1 In the illustrated embodiment, the motor 1001 and the reducer 1002 are adjacently arranged in the housing 1003 along the axial direction of the motor 1001 .

[0068] It can be understood that the various functional structural devices of the power assembly 1000 are housed and fixed in the housing 1003, so that the housing 1003 can support and fix the various functional structural devices inside it, so as to ensure that the various functional structural devices inside the power assembly 1000 can work normally, thereby ensuring the working performance of the power assembly 1000. At the same time, the housing 1003 can protect the various functional structural devices inside it, so as to prevent foreign objects such as dust and impurities in the external environment from invading the interior of the housing 1003 and possibly causing damage to the various functional structural devices inside, thereby improving the working performance and life of the power assembly 1000.

[0069] The motor 1001 is connected to the reducer 1002. The motor 1001 is used to generate driving torque and is used as a power source of the power assembly 1000 to output power. The motor 1001 transmits the output power to the wheels through the reducer 1002 to drive the vehicle to travel.

[0070] Specifically, the motor 1001 includes a stator 1006, a rotor 1007 and a motor shaft 1008. The stator 1006 is coaxially sleeved on the periphery of the rotor 1007 and fixed relative to the housing 1003 of the motor 1001. The motor shaft 1008 of the motor 1001 is coaxially fixed to the rotor 1007. The rotor 1007 rotates around its own axis and synchronously drives the motor shaft 1008 to rotate, so as to output power through the motor shaft 1008.

[0071] exist Figure 1 In the embodiment shown, the reducer 1002 includes a plurality of gears 1004 and a plurality of rotating shafts 1005, and the plurality of rotating shafts 1005 are arranged in parallel and at intervals. The plurality of gears 1004 are used to realize the transmission connection between the plurality of rotating shafts 1005, so as to transmit the power input by the motor 1001 and output it to the wheel end.

[0072] Exemplarily, the reducer 1002 further includes a plurality of bearings 10021. Two bearings 10021 are provided corresponding to one rotating shaft 1005. Specifically, along the axial direction of each rotating shaft 1005, the inner ring of each bearing 10021 is sleeved on the periphery of one end of one rotating shaft 1005, and the outer ring of each bearing 10021 can be fixed to the housing 1003. It can be understood that, through the cooperation of the two bearings 10021, a supporting and positioning effect can be formed for the rotating shaft 1005, so that the rotating shaft 1005 can be fixed relative to the housing 1003 while ensuring the rotation and transmission of the rotating shaft 1005.

[0073] Exemplarily, the plurality of rotating shafts 1005 include an input shaft 1005a, an intermediate shaft 1005b and an output shaft 1005c, wherein the input shaft 1005a, the intermediate shaft 1005b and the output shaft 1005c are arranged in parallel and at intervals. The input shaft 1005a is used for transmission connection to the motor shaft 1008 of the motor 1001, and the intermediate shaft 1005b is used for transmission connection to the output shaft 1005c through at least one gear 1004.

[0074] The gears 1004 respectively sleeved on each shaft mesh with each other to achieve the effect of connecting the intermediate shaft 1005b to the input shaft 1005a and the output shaft 1005c. The motor 1001 is used to output power to the outside. Since the motor shaft 1008 is coaxially driven with the input shaft 1005a of the reducer 1002, when the motor shaft 1008 rotates around its own axis, it will synchronously drive the input shaft 1005a to rotate coaxially, thereby achieving the effect of inputting power into the reducer 1002.

[0075] That is, the reducer 1002 is arranged adjacent to one side of the motor 1001 along the axial direction of the motor 1001, and the axis of the motor shaft 1008 coincides with the axis of the input shaft 1005a, so that the input shaft 1005a of the reducer 1002 and the motor shaft 1008 of the motor 1001 can be coaxially connected, and then the motor shaft 1008 and the input shaft 1005a cooperate with each other to achieve the effect of the motor 1001 inputting power into the reducer 1002.

[0076] The output shaft 1005c of the reducer 1002 can but is not limited to rotating coaxially with the wheel, so as to transmit the power input by the input shaft 1005a out of the reducer 1002 and to the wheel end, thereby achieving the effect of the motor 1001 driving the wheel to rotate through the reducer 1002.

[0077] The intermediate shaft 1005b is arranged parallel to and at intervals between the input shaft 1005a and the output shaft 1005c, so that the intermediate shaft 1005b realizes a transmission connection between the input shaft 1005a and the output shaft 1005c, and can transmit the power input into the reducer 1002 by the motor 1001 through the input shaft 1005a to the output shaft 1005c, and transmit it outward through the output shaft 1005c, thereby realizing the effect of the reducer 1002 transmitting the power of the motor 1001 and outputting it.

[0078] Specifically, the plurality of gears 1004 include an input gear 1004a, an intermediate transmission gear 1004b and an output gear 1004c. The input gear 1004a is sleeved on the periphery of the input shaft 1005a, the intermediate transmission gear 1004b is sleeved on the periphery of the intermediate shaft 1005b, and the output gear 1004c is sleeved on the periphery of the output shaft 1005c.

[0079] like Figure 1 As shown, the number of intermediate transmission gears 1004b sleeved on the periphery of the intermediate shaft 1005b can be multiple. Figure 1 In the illustrated embodiment, the number of intermediate transmission gears 1004b sleeved on the outer periphery of the intermediate shaft 1005b is two as an example for exemplary description. Along the axial direction of the intermediate shaft 1005b, the two intermediate transmission gears 1004b are arranged at intervals. One of the intermediate transmission gears 1004b is meshed with the input gear 1004a to transmit the power of the input shaft 1005a to the intermediate shaft 1005b. The other intermediate transmission gear 1004b is meshed with the output gear 1004c to transmit the power of the intermediate shaft 1005b to the output shaft 1005c.

[0080] That is, the motor shaft 1008 rotates and synchronously drives the input shaft 1005a to rotate, and the input shaft 1005a rotates and drives the input gear 1004a to rotate. Since the input gear 1004a is meshed with an intermediate transmission gear 1004b, the rotation of one intermediate transmission gear 1004b can drive the intermediate shaft 1005b to rotate and simultaneously drive another intermediate transmission gear 1004b to rotate. At the same time, since another intermediate transmission gear 1004b is meshed with the output gear 1004c, the rotation of the output gear 1004c can drive the output shaft 1005c to rotate. It can be understood that through the meshing between the input gear 1004a, the intermediate transmission gear 1004b and the output gear 1004c, the multiple rotating shafts 1005 can be driven to rotate, so as to achieve the effect of transmitting the power output by the motor 1001.

[0081] It should be noted that Figure 1 The embodiment shown is only an example of a possible arrangement mode and arrangement spacing between the multiple rotating shafts 1005 in the reducer 1002, and a possible arrangement number and spacing of the gears 1004 sleeved on each rotating shaft 1005, but the arrangement mode and spacing between the multiple rotating shafts 1005 in the reducer 1002, and the arrangement number and spacing of the gears 1004 sleeved on each rotating shaft 1005 are not limited to this. In other embodiments of the present application, the arrangement mode and spacing between the multiple rotating shafts 1005 in the reducer 1002, and the structural size, type, arrangement number and spacing of the gears 1004 sleeved on each rotating shaft 1005 can be adjusted according to actual design requirements, and the embodiment of the present application does not specifically limit this.

[0082] At the same time, Figure 1In the illustrated embodiment, only the possible functional structures in the powertrain 1000 provided in the embodiment of the present application and the possible structural shapes, sizes, and arrangement positions of each functional structure are used as examples for exemplary introduction, but the functional structural devices in the powertrain 1000 provided in the embodiment of the present application and the structural shapes, sizes, and arrangement positions of each functional structural device are not limited to this. In other embodiments of the present application, the functional structural devices in the powertrain 1000 and the structural shapes, sizes, and arrangement positions of each functional structural device can be adjusted according to actual design requirements and application scenarios, and the embodiment of the present application does not specifically limit this.

[0083] In one embodiment, the motor 1001 and the reducer 1002 of the power assembly 1000 provided in the embodiment of the present application may be, but not limited to, a separate type, or may be, but not limited to, an integrated type.

[0084] In one embodiment, the power output by the powertrain 1000 provided in the embodiment of the present application can be, but is not limited to, provided only by the motor 1001. When the power of the powertrain 1000 provided in the present application is provided only by the motor 1001, the powertrain 1000 of the present application can output power as a pure electric system.

[0085] See also Figure 2 , Figure 2 This is a schematic diagram of the planar structure of the powertrain 1000 provided in an embodiment of the present application. Figure 2 In the illustrated embodiment, the power assembly 1000 includes a first filter 10091, an oil pump 10092, a heat exchanger 10093, a second filter 10094, and an oil pool 10095. In the flow direction of the coolant, the oil pool 10095, the first filter 10091, the heat exchanger 10093, the oil pump 10092, and the second filter 10094 are interconnected and work in coordination with each other to realize functions such as oil supply, oil return, and coolant circulation within the power assembly 1000.

[0086] In one embodiment, the oil pool 10095 can be, but is not limited to, connected to the receiving chambers of the motor 1001, the reducer 1002 and other functional structural devices in the housing 1003. In one embodiment, the coolant delivery path arranged inside the power assembly 1000 can be used to deliver coolant to the motor 1001, the reducer 1002 and other functional structural devices to meet the lubrication and heat dissipation requirements of the various functional structural devices in the power assembly 1000, thereby ensuring the working performance and life of the power assembly 1000. Exemplarily, after the coolant has completed the heat dissipation or lubrication function of the motor 1001, the reducer 1002 and other functional structural devices, the used coolant is returned to the oil pool 10095. Alternatively, the oil pool 10095 can also be used to store oil when the external oil circuit is used to fill the housing 1003 of the power assembly 1000 with oil.

[0087] In one embodiment, the first filter 10091 is connected between the oil pump 10092 and the oil pool 10095. When the oil pump 10092 provides negative pressure and absorbs the coolant in the oil pool 10095, the coolant in the oil pool 10095 is firstly transported to the first filter 10091 for coarse filtration, so as to filter out relatively large impurities and abrasive particles mixed in the coolant, thereby improving the cleanliness of the coolant and preventing the impurities, abrasive particles and other foreign matters mixed in the coolant from damaging the oil pump 10092, thereby improving the working performance and life of the oil pump 10092.

[0088] In one embodiment, the oil pump 10092 draws coolant from the oil pool 10095 and delivers it to the heat exchanger 10093. Figure 2 In the illustrated embodiment, the heat exchanger 10093 is used to achieve heat exchange for the coolant in the powertrain 1000. After being transported to the heat exchanger 10093, the coolant carrying heat output from other structural devices in the powertrain 1000 is heat exchanged by the heat exchanger 10093 and outputs coolant with a relatively low temperature to the outside, so that the coolant can be used to achieve heat dissipation and cooling effects for the motor 1001 and other functional structural devices in the powertrain 1000, ensuring that the powertrain 1000 is at a suitable operating temperature, and improving the working performance and life of the powertrain 1000.

[0089] In one embodiment, the heat exchanger 10093 can be, but is not limited to, connected to the receiving cavities of the motor 1001, the reducer 1002 and other working structure devices, so that the heat exchanger 10093 can provide coolant to the motor 1001, the reducer 1002 and other working structure devices, respectively, for lubrication or heat dissipation of the motor 1001, the reducer 1002 and other working structure devices, thereby enabling the motor 1001, the reducer 1002 and other working structure devices to operate in a suitable temperature environment, further improving the working performance and life of the power assembly 1000.

[0090] In one embodiment, along the flow direction of the coolant, a second filter 10094 is further arranged on one side of the oil outlet of the heat exchanger 10093. The aperture of the filter screen of the second filter 10094 is smaller than the aperture of the filter screen of the first filter 10091. That is, the second filter 10094 is used to further filter impurities, abrasive particles and other foreign matter with relatively small volume, structural size, etc. in the coolant, so as to further improve the cleanliness of the coolant.

[0091] In one embodiment, a plurality of oil pipelines are arranged in the power assembly 1000 , and the plurality of oil pipelines are connected between various functional structural devices inside the power assembly 1000 to realize the coolant transportation function inside the power assembly 1000 .

[0092] For an example, please combine Figure 2 See also Figure 3 , Figure 3 This is a schematic diagram of the working principle of active lubrication of the internal coolant of the powertrain 1000 provided in the embodiment of the present application. Figure 2 and Figure 3 In the illustrated embodiment, the power assembly 1000 uses active lubrication to lubricate or dissipate heat for the motor 1001, the reducer 1002 and other power structure devices of the power assembly 1000. Exemplarily, active lubrication can be understood as the oil pump 10092 sucking the coolant in the oil pool 10095, and can be, but not limited to, sequentially transporting it to the heat exchanger 10093 for heat exchange and the second filter 10094 for fine filtering. Then, the motor 1001, the reducer 1002 and other power structure devices of the power assembly 1000 are respectively transported for lubrication or heat dissipation.

[0093] It should be noted that in Figure 2 In the illustrated embodiment, only one possible oil delivery path of the coolant in the powertrain 1000 is used as an example for illustrative description, but the oil delivery path for the coolant in the powertrain 1000 of the present application is not limited to this. Figure 2 In the illustrated embodiment, the coolant is used only for dissipating heat from the stator winding end and lubricating the gear 1004 or a bearing 10021, but the coolant is not limited to lubricating only the stator winding end of the motor 1001, the gear 1004 of the reducer 1002, or any bearing 10021 in the motor 1001 or the reducer 1002.

[0094] At the same time, Figure 2In the illustrated embodiment, only the functional device or functional structural component for conveying coolant in the power assembly 1000 of the present application is used as an example for illustrative introduction, but the layout position and structural size characteristics of each functional structural device in the power assembly 1000 are not limited to this.

[0095] In the present application specification, the example of delivering coolant to the gear 1004 or bearing 10021 of the reducer 1002 for lubrication is used for exemplary introduction. However, the powertrain 1000 provided in the embodiment of the present application is not limited to being able to only deliver coolant to the reducer for lubrication. At the same time, in the present application specification, the positions corresponding to the motor 1001, reducer 1002 and other functional structural devices of the powertrain 1000 that require coolant for lubrication are briefly described as positions to be lubricated. The position to be lubricated can be, but is not limited to, the bearing for supporting the motor shaft 1008 in the motor 1001, or the gear 1004 or bearing 10021 in the reducer 1002, or the gear or bearing in the differential.

[0096] Please also read Figure 4 and Figure 5 , Figure 4 This is a schematic diagram of the appearance structure of the powertrain 1000 provided in the embodiment of the present application with some structures hidden. Figure 5 This is a schematic diagram of the appearance of the powertrain 1000 provided in the embodiment of the present application with some structures hidden. In order to clearly illustrate the possible layout of an injection pipe 10 relative to the reducer 1002, Figure 4 and Figure 5 Functional structural devices such as the motor 1001, the oil pump 10092 and other oil pipelines of the power assembly 1000 are omitted, and only a possible layout position of an injection pipe 10 relative to the reducer 1002 is used as an example for exemplary introduction.

[0097] like Figure 4 and Figure 5 As shown, the power assembly 1000 includes a combined oil injection pipe 10, which is fixed in a housing 1003 of the power assembly 1000. The oil injection pipe 10 is used to deliver coolant to the gear 1004 or the bearing 10021 of the reducer 1002 for lubrication.

[0098] Specifically, the oil injection pipe 10 is connected to the oil delivery pipeline arranged in the housing 1003, and the oil injection pipe 10 corresponds to a position to be lubricated, so as to deliver the coolant sucked by the oil pump 10092 and delivered to the oil delivery pipeline to each position to be lubricated or each position to be cooled. It can be understood that the coolant in the oil pool 10095 is pressurized by the oil pump 10092 and then pressed into the oil delivery pipeline arranged in the power assembly 1000, and can be delivered to one oil injection pipe 10 through the oil delivery pipeline, but is not limited to, so as to be delivered to each position to be lubricated through one oil injection pipe 10.

[0099] exist Figure 4 and Figure 5 In the illustrated embodiment, the fuel injection pipe 10 includes an integrally formed fuel delivery pipe 11, which includes an fuel inlet pipe 111 and a plurality of fuel outlet pipes 112. The plurality of fuel outlet pipes 112 are used to receive coolant through the fuel inlet pipe 111, and each fuel outlet pipe 112 is used to output coolant to lubricate at least one of the gears 1004 or bearings 10021 of the reducer 1002.

[0100] It can be understood that the powertrain 1000 is equipped with a fuel injection pipe 10, which can transport coolant to lubricate the transmission structure in the powertrain 1000, so as to improve the working performance and life of the transmission mechanism. The fuel injection pipe 10 is fixedly connected to the housing 1003, and the housing 1003 can form a supporting effect on the fuel injection pipe 10, ensuring that the fuel injection pipe 10 can stably and continuously transport coolant to the lubricated position in the powertrain 1000, and avoid the fuel injection pipe 10 from shaking, shifting and other undesirable phenomena during the operation of the powertrain 1000. That is, the housing 1003 forms a supporting and fixing effect on the fuel injection pipe 10, which can improve the precision and accuracy of the fuel injection pipe 10 in transporting coolant.

[0101] In one embodiment, the oil pipeline 11 is an injection molded part. The oil pipeline 11 is prepared by an injection molding process, so that the oil pipeline 11 is formed in one piece, which reduces the difficulty of preparing the oil pipeline 11 and improves the preparation efficiency of the oil pipeline 11, thereby improving the overall preparation efficiency of the power assembly 1000. At the same time, the material of the injection molded part is usually rubber or plastic with a relatively small weight. Therefore, preparing the oil pipeline 11 by an injection molding process can reduce the weight of the oil pipeline 11, thereby reducing the overall weight of the power assembly 1000, so as to meet the lightweight design requirements of the power assembly 1000.

[0102] That is, the oil pipe 11 is integrally formed by the injection molding process, so that the oil pipe 11 can transport coolant to multiple locations to be lubricated while taking into account the lightweight design requirements of the powertrain 1000.

[0103] Please also read Figure 6 and Figure 7 , Figure 6This is a schematic diagram of the appearance structure of the fuel injection pipe 10 of the power assembly 1000 provided in an embodiment of the present application. Figure 7 Schematic diagram of the planar structure of the fuel injection pipe 10 of the power assembly 1000 provided in the embodiment of the present application. Figure 6 and Figure 7 As shown, the oil inlet pipe 111 simultaneously delivers the coolant to the multiple oil outlet pipes 112, and the coolant is delivered to different positions to be lubricated in the reducer 1002 through the multiple oil outlet pipes 112. That is, the cooling oil is delivered to the outer peripheries of different gears 1004 or different bearings 10021 of the reducer 1002 through the multiple oil outlet pipes 112 for lubrication.

[0104] Specifically, the extension direction of the oil inlet pipe 111 intersects with the extension direction of each oil outlet pipe 112. Figure 6 and Figure 7 In the illustrated embodiment, each oil outlet pipe 112 is connected to the outer peripheral wall 111a of the oil inlet pipe 111. The plurality of oil outlet pipes 112 are spaced apart from each other along the direction in which the coolant flows in the oil inlet pipe 111. That is, the plurality of oil outlet pipes 112 are spaced apart along the direction in which the oil inlet pipe 111 extends, and the opening of each oil outlet pipe 112 for receiving the coolant is connected to the outer peripheral wall 111a of the oil inlet pipe 111.

[0105] It can be understood that multiple oil outlet pipes 112 are arranged in the extension direction of the oil inlet pipe 111, and the multiple oil outlet pipes 112 are arranged at intervals along the extension direction of the oil inlet pipe 111, so that the oil inlet pipe 111 can simultaneously transport coolant to the multiple oil outlet pipes 112, so as to improve the lubrication and heat dissipation efficiency of the fuel injection pipe 10 for the power assembly 1000, while also reducing the structural dimensions of the fuel injection pipe 10 along the extension direction of the oil inlet pipe 111, thereby simplifying the internal structure design of the power assembly 1000.

[0106] In one embodiment, the aperture D1 of the oil inlet pipe 111 is larger than the aperture D2 of any oil outlet pipe 112 among the multiple oil outlet pipes 112 , and the interval between any two adjacent oil outlet pipes 112 among the multiple oil outlet pipes 112 is larger than the aperture D2 of any oil outlet pipe 112 among the two oil outlet pipes 112 .

[0107] It can be understood that since the oil inlet pipe 111 is used to transport coolant to multiple oil outlet pipes 112 at the same time, by setting the aperture D1 of the oil inlet pipe 111 to be larger than the aperture D2 of any of the multiple oil outlet pipes 112, the flow rate of coolant in the oil inlet pipe 111 can be greater than the flow rate of coolant in each oil outlet pipe 112, which can ensure that the oil injection pipe 10 can transport sufficient coolant to each position to be lubricated, so as to ensure the lubrication effect of each position to be lubricated, thereby further improving the working efficiency and life of the powertrain 1000.

[0108] In one embodiment, the angle P between the extension direction of each oil outlet pipe 112 and the direction of coolant flow in an oil inlet pipe 111 is less than or equal to 90°. Figure 6 and Figure 7 As shown, the extension direction of each oil outlet pipe 112 is the same as the direction of coolant flow, which can avoid turbulence that may occur in an oil inlet pipe 111 and affect the smooth flow of the coolant, thereby improving the stability and efficiency of coolant delivery from an oil inlet pipe 111 to each oil outlet pipe 112.

[0109] It should be noted that in Figure 7 In the illustrated embodiment, only one possible number, direction, extension length and aperture of the oil outlet pipe 112 of the oil injection pipe 10 is used as an example for illustrative description, but the number of arrangement, arrangement interval, and the direction, extension length and aperture of each oil outlet pipe 112 of the oil injection pipe 10 of the present application are not limited to this. In other embodiments of the present application, the number of arrangement and the intervals between the multiple oil outlet pipes 112 of the oil injection pipe 10, as well as the direction, extension length and aperture of each oil outlet pipe 112, can be adjusted according to the actual use scenario and design requirements of the oil injection pipe 10, and the embodiments of the present application do not specifically limit this.

[0110] Please combine Figure 6 and Figure 7 See also Figure 8 , Figure 8 This is a schematic diagram of the partial appearance structure of the powertrain 1000 provided in the embodiment of the present application. Figure 6-Figure 8 In the illustrated embodiment, the housing 1003 includes an oil delivery hole 10031 for delivering coolant to the plurality of oil outlet pipes 112 through the oil inlet pipe 111. The oil inlet pipe 111 includes an oil inlet port 111b for receiving the coolant delivered by the oil delivery hole 10031.

[0111] Exemplarily, the oil delivery hole 10031 may be, but is not limited to, connected to an oil delivery pipeline in the housing 1003 , so as to deliver the coolant in the oil delivery pipeline to the fuel injection pipe 10 .

[0112] In one embodiment, along the direction of coolant flow in the oil inlet pipe 111, the oil inlet port 111b is located on the same side of the opening of each oil outlet pipe 112 connected to the oil inlet pipe 111. Figure 6-Figure 8 As shown, along the extension direction of the oil inlet pipe 111, the oil inlet port 111b is opened at one end of the oil inlet pipe 111, so that the coolant delivered from the oil delivery hole 10031 can be input into the oil inlet pipe 111 from one end thereof. Then, along the flow direction of the coolant in the oil inlet pipe 111, the coolant is sequentially delivered to each oil outlet pipe 112 connected to the outer peripheral wall 111a of the oil inlet pipe 111 through the oil inlet pipe 111.

[0113] It can be understood that the coolant input from the oil delivery hole 10031 of the housing 1003 is received through the oil inlet 111b, and the coolant is delivered from one end of the oil inlet pipe 111 to each oil outlet pipe 112 in sequence, which can reduce the turning or diversion of the coolant in the oil inlet pipe 111, and improve the stability and stability of the coolant delivery from the oil inlet pipe 111 to each oil outlet pipe 112, while ensuring that the flow rate of the coolant delivered from the oil inlet pipe 111 to each oil outlet pipe 112 can meet the lubrication requirements of the lubricated position. At the same time, arranging multiple oil outlet pipes 112 on the same side of the oil inlet 111b can further reduce the structural size of the injection pipe 10 to further realize the miniaturization design of the injection pipe 10.

[0114] Please combine Figure 6-Figure 8 See also Fig. 9 and Fig.10 , Fig. 9 This is a schematic diagram of the appearance structure of the powertrain 1000 provided in the embodiment of the present application with some structures hidden. Fig.10 This is a schematic diagram of the external structure of the powertrain 1000 provided in the embodiment of the present application with some structures hidden. In order to clearly illustrate the layout position of the fuel injection pipe 10 relative to the multiple gears 1004 and the multiple shafts 1005 in the reducer 1002, Fig. 9 and Fig.10 The housing 1003 and other possible functional components of the power assembly 1000 are hidden.

[0115] like Figure 6-Figure 10 As shown, multiple oil outlet pipes 112 are used to deliver coolant to the outer peripheries of multiple gears 1004 or multiple bearings 10021 in the reducer 1002. The multiple gears 1004 and multiple bearings 10021 in the reducer are respectively arranged corresponding to the rotating shaft 1005 at different positions in the reducer 1002, so the multiple gears 1004 and multiple bearings 10021 are distributed in different positions and directions in the housing 1003.

[0116] Exemplarily, the oil injection pipe 10 includes a first oil outlet pipe 112a, which faces the meshing surface of the input gear 1004a and the intermediate transmission gear 1004b of the reducer 1002 to deliver coolant to the input gear 1004a and the intermediate transmission gear 1004b for lubrication.

[0117] Exemplarily, the oil injection pipe 10 includes a second oil outlet pipe 112 b, which faces the bearing 10021 of the intermediate shaft 1005 b of the reducer 1002 so as to deliver coolant to the outer periphery of the bearing 10021 for lubrication.

[0118] Exemplarily, the oil injection pipe 10 includes a third oil outlet pipe 112c, which faces the meshing surface of the output gear 1004 of the reducer 1002 and another intermediate transmission gear 1004b to deliver coolant to the outer periphery of the output gear 1004 and another intermediate transmission gear 1004b for lubrication.

[0119] It should be noted that in Fig. 9 and Fig.10 In the illustrated embodiment, only the first oil outlet pipe 112a, the second oil outlet pipe 112b and the third oil outlet pipe 112c are used to distinguish the oil outlet pipes 112 in different directions, and the oil outlet pipes 112 in different directions respectively transport coolant to different gears 1004 or bearings 10021 of the reducer 1002 for lubrication. However, it is not limited that the first oil outlet pipe 112a, the second oil outlet pipe 112b and the third oil outlet pipe 112c have a limited relationship with the gears 1004 or bearings 10021 at specific positions in the reducer 1002, that is, it is not limited that the first oil outlet pipe 112a, the second oil outlet pipe 112b and the third oil outlet pipe 112c have a corresponding relationship in structure shape and size. That is, in the embodiment of the present application, corresponding to the gears 1004 and bearings 10021 in the reducer 1002 distributed in different positions and directions in the housing 1003, the orientation and structural dimensions of the oil outlet pipe 112 of the injection pipe 10 can be adjusted to meet the usage and design requirements of the powertrain 1000.

[0120] In one embodiment, along the direction of coolant flow in each oil outlet pipe 112, the distance between each oil outlet pipe 112 and the gear 1004 or the bearing 10021 of the reducer 1002 is less than or equal to 30 mm. Figure 6-Figure 10 As shown, by setting the interval between each oil outlet pipe 112 and the gear 1004 or bearing 10021 of the reducer 1002 to be less than or equal to 30 mm, the coolant output by each oil outlet pipe 112 can be reduced from being affected by other factors and may cause adverse phenomena such as conveying path deviation, thereby ensuring the accuracy and efficiency of the oil injection pipe 10 in conveying coolant to each position to be lubricated.

[0121] Please also read Figure 11-13 , Fig.11 This is a schematic diagram of the appearance structure of the fuel injection pipe 10 of the power assembly 1000 provided in an embodiment of the present application. Fig.12 This is a schematic diagram of the appearance structure of the fuel injection pipe 10 of the power assembly 1000 provided in an embodiment of the present application. Fig.13 Schematic diagram of a partial cross-sectional structure of the fuel injection pipe 10 of the power assembly 1000 provided in the embodiment of the present application. Figure 11-13As shown, the oil injection pipe 10 also includes a plurality of combined nozzles 12, and the plurality of nozzles 12 correspond one to one with the plurality of oil inlet pipes 111. Along the direction of the coolant flow, each nozzle 12 corresponds to one oil inlet pipe 111, one end 12a of each nozzle 12 is fixedly connected to one oil inlet pipe 111 and is used to receive the coolant output by the oil inlet pipe 111, and the opening of the other end 12b of each nozzle 12 is used to transport the coolant to the gear 1004 or the bearing 10021 of the reducer 1002 for lubrication.

[0122] For example, along the direction of coolant flow, the nozzle 12 is fixedly connected to the oil outlet pipe 112 at one end 12a facing the oil outlet pipe 112, and the opening of the nozzle 12 at one end 12a close to the oil outlet pipe 112 can receive the coolant output by the oil outlet pipe 112. At the same time, the other end 12b of the nozzle 12 facing away from the oil outlet pipe 112 faces the position to be lubricated, that is, the opening of the other end 12b faces the gear 1004 or the bearing 10021 in the reducer 1002, so that the coolant can be delivered to the outer periphery of the gear 1004 or the bearing 10021 of the reducer 1002 for lubrication.

[0123] In one embodiment, the aperture D3 of the opening at one end 12a of one of the multiple nozzles 12 is larger than the aperture D2 of the oil outlet pipe 112, and larger than the aperture D4 of the opening at the other end 12b of the nozzle 12. For ease of description, in the present specification, the nozzle 12 whose aperture D3 of the opening at one end 12a of the multiple nozzles 12 facing the oil outlet pipe 112 is larger than the aperture D4 of the opening at the other end 12b is illustrated as the first nozzle 121.

[0124] That is, in Figure 11-13 In the illustrated embodiment, the aperture D3 of the opening of the first nozzle 121 toward one end 121a of the oil outlet pipe 112 is larger than the aperture D4 of the opening of the other end 121b of the first nozzle 121 away from the oil outlet pipe 112. For example, the aperture of the first nozzle 121 may be, but is not limited to, gradually reduced along the direction of coolant flow.

[0125] It is difficult to ensure the accuracy of the fuel injection pipe installed in the powertrain in delivering coolant to multiple locations to be lubricated at the same time, and the structural complexity and preparation difficulty of the fuel injection pipe are increased.

[0126] The multiple oil outlet pipes 112 of the oil injection pipe 10 of the power assembly 1000 of the present application respectively correspond to the positions to be lubricated at different positions of the transmission structure in the power assembly 1000, so as to simultaneously deliver coolant to different positions to be lubricated for lubrication. For example, the multiple oil outlet pipes 112 can be used to deliver coolant to the gears 1004 and bearings 10021 at different positions of the reducer 1002 for lubrication, which can improve the lubrication efficiency of the oil injection pipe 10. The oil injection pipe 10 delivers coolant to the multiple oil outlet pipes 112 at the same time through the oil inlet pipe 111, which improves the efficiency of the oil inlet pipe 111 in delivering coolant to the multiple oil outlet pipes 112.

[0127] At the same time, multiple oil outlet pipes 112 are simultaneously connected to the outer peripheral wall 111a of the oil inlet pipe 111, and the oil inlet pipe 111 and multiple oil outlet pipes 112 are prepared in an integrated manner, which simplifies the structural design of the oil delivery pipe 11 and reduces the difficulty of preparing the oil delivery pipe 11 to improve the preparation efficiency of the oil injection pipe 10. The first nozzle 121 of the oil injection pipe 10 corresponds to the oil outlet pipe 112, and the coolant output by the oil outlet pipe 112 is delivered to the gear 1004 or the outer periphery of the bearing 10021 of the reducer 1002 through the first nozzle 121 for lubrication.

[0128] Along the direction of coolant flow, since the aperture D4 of the opening of the other end 121b of the first nozzle 121 is smaller than the aperture D3 of the opening of the one end 121a of the first nozzle 121, the pressure of the coolant at the other end 121b of the first nozzle 121 is greater than the pressure of the coolant at the one end 121a of the first nozzle 121, thereby achieving the effect of increasing the pressure of the output coolant. When the distance between the oil outlet pipe 112 and its corresponding position to be lubricated is far or the viscosity of the coolant is too high at low temperature, the position to be lubricated, such as the gear 1004 or the bearing 10021 in the reducer 1002, can be increased by increasing the pressure of the coolant output by the first nozzle 121, so as to increase the delivery distance and output flow rate of the coolant delivered by the oil outlet pipe 112, thereby ensuring that the oil outlet pipe 112 can accurately deliver the coolant to the position to be lubricated and ensure that the oil outlet pipe 112 delivers a sufficient flow rate of coolant to the position to be lubricated for lubrication.

[0129] At the same time, the split design of the oil delivery pipe 11 and the first nozzle 121 of the fuel injection pipe 10 can not only ensure the precision and accuracy of the fuel injection pipe 10 in delivering the coolant, but also simplify the structure of the fuel injection pipe 10, reduce the difficulty and cost of preparing the fuel injection pipe 10, and improve the preparation efficiency of the fuel injection pipe 10.

[0130] The vehicle of the present application is equipped with the powertrain 1000 in any of the above-mentioned implementations, which can improve the working performance and life of the vehicle of the present application. Or, the vehicle of the present application is equipped with the fuel injection pipe 10 in any of the above-mentioned implementations, which can improve the working efficiency and life of the vehicle. That is, because the powertrain 1000 in any of the above-mentioned implementations or the fuel injection pipe 10 in any of the above-mentioned implementations is used, the vehicle of the present application has all the possible beneficial effects of the powertrain 1000 provided by any of the above-mentioned implementations or the fuel injection pipe 10 provided by any of the above-mentioned implementations.

[0131] In one embodiment, along the direction of coolant flow, the first nozzle 121 includes two connected sections, one section 1211 is used to receive the coolant delivered by the oil outlet pipe 112 and to deliver it to the other section 1212, and the other section 1212 is used to output the coolant. In the direction of coolant flow, the aperture of one section 1211 gradually decreases along the direction of coolant flow, and the aperture of the other section 1212 is less than or equal to the minimum aperture of one section 1211.

[0132] It can be understood that along the direction of the coolant flow, one section 1211 is closer to the oil outlet pipe 112 than the other section 1212, and the aperture of one section 1211 gradually decreases, so that after receiving the coolant output by the oil outlet pipe 112, one section 1211 gradually increases the pressure of the coolant. That is, one section 1211 gradually increases the pressure of the coolant by setting its aperture to gradually decrease along the direction of the coolant flow, thereby improving the flow stability and smoothness of the coolant in the first nozzle 121.

[0133] The aperture of the other section 1212 is smaller than or equal to the aperture of one section 1211, and the aperture of the other section 1212 remains unchanged, so that the coolant with increased pressure can be stably and accurately delivered from the other section 1212 to the lubrication position, further improving the stability and accuracy of the first nozzle 121 in delivering the coolant.

[0134] In one embodiment, the extension length L1 of one section 1211 is greater than the extension length L2 of the other section 1212. Along the direction of coolant flow, the extension lengths of one section 1211 and the other section 1212 of the first nozzle 121 are set differently, which can improve the stability and accuracy of the coolant output by the first nozzle 121 while reducing the structural dimensions of the first nozzle 121 along the direction of coolant flow, so as to achieve the effect of miniaturized design of the first nozzle 121.

[0135] In one embodiment, along the direction of the coolant flow, the axis of the first nozzle 121 coincides with the axis of the oil outlet pipe 112. The oil outlet pipe 112 is connected to one end 121a of the first nozzle 121 by welding.

[0136] It can be understood that the end 121a of the first nozzle 121 and the oil outlet pipe 112 are fixed by welding, and there is no need to design an additional structure between the oil outlet pipe 112 and the first nozzle 121 to achieve the fixation between the two, which can further simplify the structural design of the first nozzle 121 and the oil outlet pipe 112. In addition, the first nozzle 121 and the oil outlet pipe 112 are fixed by welding, which simplifies the structure of the first nozzle 121 and the oil outlet pipe 112 and improves the stability and reliability of the mutual fixation of the first nozzle 121 and the oil outlet pipe 112.

[0137] Please combine Fig.13 See also Fig.14 and Fig.15 , Fig.14 This is a schematic diagram of a partial cross-sectional structure of a fuel injection pipe 10 of a power assembly 1000 provided in an embodiment of the present application. Fig.15 This is a schematic diagram of the planar structure of a nozzle 12 of the power assembly 1000 provided in an embodiment of the present application. Figure 13-Figure 15 In the illustrated embodiment, the first nozzle 121 includes two first annular protrusions 1213, and the two first annular protrusions 1213 extend in directions away from each other along the axial direction of the first nozzle 121. Specifically, along the direction of coolant flow, one of the first annular protrusions 1213a is protruded from one end 121a of the first nozzle 121 facing the oil outlet pipe 112, and the other first annular protrusion 1213b is protruded from the other end 121b of the first nozzle 121 away from the oil outlet pipe 112.

[0138] That is, if Figure 13-Figure 15 As shown, along the direction of coolant flow, two first annular protrusions 1213 are arranged on both sides of the first nozzle 121, one of the first annular protrusions 1213a is closer to the oil outlet pipe 112 than the other first annular protrusion 1213b, and the other first annular protrusion 1213b faces the gear 1004 or the bearing 10021 of the reducer 1002. Figure 13-Figure 15 In the illustrated embodiment, along the direction of coolant flow, the first annular protrusion 1213 that is closer to the oil outlet pipe 112 of the two first annular protrusions 1213 is illustrated as one of the first annular protrusions 1213a, and the first annular protrusion 1213 that is farther away from the oil outlet pipe 112 of the two first annular protrusions 1213 is illustrated as the other first annular protrusion 1213b.

[0139] In one embodiment, along the direction of coolant flow, one of the first annular protrusions 1213 a is located at one end 121 a of the first nozzle 121 , and one of the first annular protrusions 1213 a is welded and fixed to the end surface of the oil outlet pipe 112 facing the first nozzle 121 .

[0140] For example, along the direction of coolant flow, one of the first annular protrusions 1213a is protruded from the end surface of the first nozzle 121 facing the oil outlet pipe 112, and extends toward the oil outlet pipe 112 along the axial direction of the first nozzle 121. The first nozzle 121 is welded to the end surface of the oil outlet pipe 112 through one of the first annular protrusions 1213a, which can improve the welding efficiency and accuracy of the first nozzle 121 and the oil outlet pipe 112.

[0141] Exemplarily, one of the first annular protrusions 1213a is disposed around the periphery of the opening of one end 121a of the first nozzle 121. Figure 13-Figure 15 As shown, along the radial direction of the oil outlet pipe 112 , the inner diameter of one of the first annular protrusions 1213 a is larger than the inner diameter of the oil outlet pipe 112 , and the outer diameter of one of the first annular protrusions 1213 a is smaller than the outer diameter of the oil outlet pipe 112 .

[0142] That is, along the direction of coolant flow, the projection of one of the first annular protrusions 1213a on the end surface of the oil outlet pipe 112 is contained within the end surface of the oil outlet pipe 112, so that one of the first annular protrusions 1213a can form a containing effect on the coolant at the connection position between the oil outlet pipe 112 and the first nozzle 121, thereby improving the efficiency and effect of conveying coolant from the oil outlet pipe 112 to the first nozzle 121.

[0143] In one embodiment, the outer diameter of the other first annular protrusion 1213b is smaller than the outer diameter of one of the first annular protrusions 1213a, and smaller than or equal to the inner diameter of one of the first annular protrusions 1213a. Figure 13-Figure 15 In the illustrated embodiment, along the direction of coolant flow, the aperture D4 of the opening of the other end 121b of the first nozzle 121 is smaller than the aperture D3 of the opening of the one end 121a of the first nozzle 121. At this time, the outer diameter of the other end 121b of the first nozzle 121 is smaller than the outer diameter of the one end 121a of the first nozzle 121, so as to simplify the structural design of the first nozzle 121 and reduce the overall weight of the first nozzle 121.

[0144] It can be understood that since one end 121a of the first nozzle 121 is welded to the oil outlet pipe 112, by reducing the weight of the other end 121b of the first nozzle 121, the welding stability and reliability of the first nozzle 121 and the oil outlet pipe 112 can be improved, thereby avoiding the undesirable phenomenon that the welding position between the first nozzle 121 and the oil outlet pipe 112 may break due to the other end 121b of the first nozzle 121 being too heavy.

[0145] In one embodiment, the oil outlet pipe 112 includes two second annular protrusions 1121, such as Figure 13-Figure 15As shown, along the direction of coolant flow, two second annular protrusions 1121 are protruded from the end surface of the oil outlet pipe 112 facing a first nozzle 121 .

[0146] Along the radial direction of the oil outlet pipe 112, two second annular protrusions 1121 are arranged at intervals, and one second annular protrusion 1121a is located inside the other second annular protrusion 1121b. Figure 13-Figure 15 In the illustrated embodiment, of the two second annular protrusions 1121, the second annular protrusion 1121 closer to the axis of the oil outlet pipe 112 is illustrated as one of the second annular protrusions 1121a, and the second annular protrusion 1121 farther from the axis of the oil outlet pipe 112 is illustrated as the other second annular protrusion 1121b.

[0147] Exemplarily, along the radial direction of the oil outlet pipe 112, the inner diameter of one of the second annular protrusions 1121a is greater than or equal to the aperture D2 of the oil outlet pipe 112, and the outer diameter of one of the second annular protrusions 1121a is less than or equal to the inner diameter of one of the first annular protrusions 1213a. Specifically, along the direction of coolant flow, one of the second annular protrusions 1121a is located inside one of the first annular protrusions 1213a, and one of the second annular protrusions 1121a at least partially overlaps with one of the first annular protrusions 1213a in the direction of coolant flow.

[0148] Exemplarily, along the direction of coolant flow, an extension length of one of the second annular protrusions 1121a is less than or equal to an extension length of one of the first annular protrusions 1213a.

[0149] It can be understood that since excess solder may be generated when one of the first annular protrusions 1213a is welded to the oil outlet pipe 112, one of the second annular protrusions 1121a is arranged to be located inside one of the first annular protrusions 1213a, that is, one of the second annular protrusions 1121a is closer to the axis of the oil outlet pipe 112 than one of the first annular protrusions 1213a, so that one of the second annular protrusions 1121a can block and contain possible excess solder, thereby preventing the excess solder that may be generated during welding from clogging the oil outlet pipe 112 or the first nozzle 121.

[0150] That is, one of the second annular protrusions 1121a of the oil outlet pipe 112 and one of the first annular protrusions 1213a of the first nozzle 121 are matched with each other, which can not only ensure the welding reliability of the first nozzle 121 and the oil outlet pipe 112, but also improve the connectivity between the first nozzle 121 and the oil outlet pipe 112, thereby improving the delivery efficiency and reliability of the coolant.

[0151] In addition, by setting one of the second annular protrusions 1121a, one of the first annular protrusions 1213a and the oil outlet pipe 112 can be positioned during welding, thereby improving the alignment effect of the first nozzle 121 and the oil outlet pipe 112, thereby further improving the accuracy and efficiency of the oil injection pipe 10 in delivering coolant to the position to be lubricated.

[0152] In one embodiment, another second annular protrusion 1121b is disposed around one of the second annular protrusions 1121a in the radial direction of the oil outlet pipe 112. Specifically, in the radial direction of the oil outlet pipe 112, the inner diameter of the other second annular protrusion 1121b is greater than or equal to the outer diameter of one of the first annular protrusions 1213a.

[0153] It can be understood that the other second annular protrusion 1121b is located at the periphery of one of the second annular protrusions 1121, and one of the second annular protrusions 1121a and the other second annular protrusion 1121b are arranged at intervals along the radial direction of the oil outlet pipe 112, so as to form an annular groove structure between one of the second annular protrusions 1121a and the other second annular protrusion 1121b. The groove structure formed between the two second annular protrusions 1121 can accommodate one of the first annular protrusions 1213a of the first nozzle 121, so as to form a avoidance effect for one of the first annular protrusions 1213a, thereby reducing the structural dimensions of the oil outlet pipe 112 and the first nozzle 121 along the direction of coolant flow, and realizing the miniaturized design of the oil injection pipe 10.

[0154] In one embodiment, along the direction of coolant flow, the extension length of another second annular protrusion 1121b is less than or equal to the extension length of one of the first annular protrusions 1213a, and greater than the extension length of one of the second annular protrusions 1121a. Figure 13-Figure 15 In the illustrated embodiment, along the direction of coolant flow, the extension length of one of the first annular protrusions 1213a of the first nozzle 121 is greater than the extension length of each of the second annular protrusions 1121, so that after one of the first annular protrusions 1213a extends into the groove structure, it can abut against the end face of the oil outlet pipe 112 facing the first nozzle 121 to be fixed by welding.

[0155] In one embodiment, along the radial direction of the oil outlet pipe 112, the interval between one second annular protrusion 1121a and another second annular protrusion 1121b is greater than the thickness of one first annular protrusion 1213a.

[0156] like Fig.14 and Fig.15As shown, along the radial direction of the oil outlet pipe 112, a gap is formed between one of the first annular protrusions 1213a and each of the second annular protrusions 1121, so that one of the first annular protrusions 1213a and the two second annular protrusions 1121 cooperate with each other, and the gap is used to accommodate excess solder that may be generated when the first nozzle 121 and the oil outlet pipe 112 are welded, thereby improving the accommodation effect of possible excess solder and further improving the connection effect between the first nozzle 121 and the oil outlet pipe 112.

[0157] In one embodiment, the thickness of one of the second annular protrusions 1121a is less than or equal to the thickness of the other second annular protrusion 1121b. Of the two second annular protrusions 1121, one of the second annular protrusions 1121a closer to the axis of the oil outlet pipe 112 is thinner than the other second annular protrusion 1121b, which can reduce the overall weight of the fuel injection pipe 10 and achieve the effect of miniaturized design of the fuel injection pipe 10.

[0158] Please also read Fig.16 and Fig.17 , Fig.16 This is a schematic plan view of the structure of another nozzle 12 of the power assembly 1000 provided in an embodiment of the present application. Fig.17 This is a schematic diagram of the planar structure of another nozzle 12 of the power assembly 1000 provided in the embodiment of the present application. Fig.16 and Fig.17 In the illustrated embodiment, the oil injection pipe 10 further includes another combined nozzle 12, one end 12a of the other nozzle 12 is used to fixedly connect another oil outlet pipe 112 among the multiple oil outlet pipes 112 and to receive the coolant delivered by the other oil outlet pipe 112, the opening of the other end 12b of the other nozzle 12 is used to deliver the coolant to lubricate another gear 1004 or another bearing 10021 of the reducer 1002, and the other end 12b of the other nozzle 12 is flat-mouthed. For ease of description, in the present specification, the other nozzle 12 with a flat-mouthed structure is illustrated as the second nozzle 122.

[0159] like Fig.16 and Fig.17 As shown, along the direction of coolant flow, the length dimension L3 of the opening of the other end 122b of the second nozzle 122 is greater than the aperture D2 of the oil outlet pipe 112, and the width dimension W of the opening of the other end 122b of the second nozzle 122 is less than the aperture D2 of the oil outlet pipe 112.

[0160] It can be understood that by providing a second nozzle 122 at one end of the oil outlet of another oil outlet pipe 112 of the plurality of oil outlet pipes 112, the opening of the other end 122b of the second nozzle 122 facing the position to be lubricated is configured as a flat mouth shape, so that the output shape of the coolant output by the second nozzle 122 can be changed. By setting the opening of the other end 122b of the second nozzle 122 as a flat mouth shape, the coolant beam output by the second nozzle 122 is squeezed in the length direction of the opening of the other end 122b of the second nozzle 122, so as to achieve the diffusion of the sprayed coolant beam and expand the coverage of the tooth surface.

[0161] That is, the shape of the coolant output from the second nozzle 122 is approximately linear or rectangular, so that the shape of the coolant output from the second nozzle 122 can match and adapt to the shape of the position to be lubricated, so as to increase the coverage area of ​​the coolant output from the second nozzle 122. By setting the opening of the other end 122b of the second nozzle 122 to be flat, the efficiency of the oil injection pipe 10 in conveying coolant to lubricate the position to be lubricated can be further improved, and the loss of coolant can be reduced to save the cost of the power assembly 1000.

[0162] At the same time, the oil delivery pipe 11 and the second nozzle 122 of the fuel injection pipe 10 are designed in a split manner, which can not only ensure the coverage area of ​​the fuel injection pipe 10 for delivering coolant, but also simplify the structure of the fuel injection pipe 10, reduce the difficulty and cost of preparing the fuel injection pipe 10, and improve the preparation efficiency of the fuel injection pipe 10.

[0163] In one embodiment, along the direction of coolant flow, the center line of the second nozzle 122 coincides with the axis of the oil outlet pipe 112. The oil outlet pipe 112 is connected to one end 122a of the second nozzle 122 by welding. One end 122a of the second nozzle 122 and the oil outlet pipe 112 are fixed by welding, and there is no need to design an additional structure between the oil outlet pipe 112 and the second nozzle 122 to achieve the fixation between the two, which can further simplify the structural design of the second nozzle 122 and the oil outlet pipe 112. In addition, the second nozzle 122 and the oil outlet pipe 112 are fixed by welding, which can simplify the structure of the second nozzle 122 and the oil outlet pipe 112 while improving the stability and reliability of the fixation between the second nozzle 122 and the oil outlet pipe 112.

[0164] In one embodiment, along the direction of the coolant flow, the opening of the other end 122b of the second nozzle 122 faces the gear 1004. Also, along the direction of the coolant flow, the length direction of the opening of the other end 122b of the second nozzle 122 is parallel to the axial direction of the gear 1004.

[0165] It can be understood that, since the length direction of the meshing surface between the gear 1004 and the other gear 1004 is parallel to the axial direction of the gear 1004, the length direction of the opening of the other end 122b of the second nozzle 122 is set to be parallel to the length direction of the meshing surface between the gear 1004 and the other gear 1004, so that the length direction of the linear or rectangular coolant output by the second nozzle 122 is parallel to the length direction of the meshing surface. The coverage area of ​​the position to be lubricated by the coolant output by the second nozzle 122 can be increased, and the lubrication efficiency of the position to be lubricated by the coolant output by the oil injection pipe 10 can be increased, and the working performance and life of the power assembly 1000 can be further improved.

[0166] See also Fig.18 , Fig.18 This is a schematic diagram of the appearance structure of the oil guide groove 13 of the power assembly 1000 provided in the embodiment of the present application. Fig.18 In the illustrated embodiment, the oil injection pipe 10 further includes an oil guide groove 13, and the oil guide groove 13 is connected to one of the plurality of oil outlet pipes 112. Specifically, along the direction of the flow of the coolant, the oil guide groove 13 is used to receive the coolant output by the oil outlet pipe 112, and is used to guide the coolant to the gear 1004 or the bearing 10021 of the reducer 1002. That is, the coolant output by the oil outlet pipe 112 is guided to the gear 1004 or the bearing 10021 of the reducer 1002 through the oil guide groove 13, which can form an effect of increasing the extension length of the oil outlet pipe 112 along the flow direction of the coolant.

[0167] It is understandable that by adding an oil guide groove 13 on one side of the oil outlet pipe 112 where the coolant is output, and guiding the coolant in the oil outlet pipe 112 to the gear 1004 or the bearing 10021 of the reducer 1002 through the oil guide groove 13, the accuracy of the oil outlet pipe 112 in delivering the coolant to the position to be lubricated in the power assembly 1000 can be further improved, thereby improving the delivery efficiency and effect of the coolant to the position to be lubricated. By increasing the extension length of the oil outlet pipe 112 along the flow direction of the coolant, the fuel injection pipe 10 in the power assembly 1000 can meet the delivery requirements of the coolant under different working conditions, which can expand the use scope and application scenarios of the fuel injection pipe 10 and improve the applicability of the fuel injection pipe 10.

[0168] In addition, while the oil guide groove 13 realizes the function of conveying coolant, it can also reduce the weight of the fuel injection pipe 10 due to its non-closed pipe structure, thereby further improving the lightweight design of the powertrain 1000.

[0169] At the same time, since the extension length of the oil guide groove 13 is not limited by the aperture ratio during the preparation process, the preparation difficulty of the oil guide groove 13 is lower than that of the oil outlet pipe 112 with a larger aperture ratio. Therefore, by providing the oil guide groove 13, the preparation difficulty of the oil outlet pipe 112 can be further reduced, and the overall extension length of the oil outlet pipe 112 can be further increased, so as to ensure that the overall extension length of the oil outlet pipe 112 meets the delivery requirements of the coolant under different working conditions, and at the same time, the preparation difficulty and requirements of the oil injection pipe 10 can be further reduced.

[0170] In one embodiment, the oil outlet pipe 112 and the oil guide groove 13 are integrally formed.

[0171] In one embodiment, at least one of the groove depth or the groove width of the oil guide groove 13 is greater than or equal to half of the hole diameter D2 of the oil outlet pipe 112 .

[0172] exist Fig.18 In the embodiment shown, along the circumference of the oil outlet pipe 112, the maximum size of the notch of the oil guide groove 13 is less than or equal to half of the circumference of the oil outlet pipe 112, which can improve the containment effect of the oil guide groove 13 on the coolant, avoid the undesirable phenomenon that the coolant may leak out from the notch of an oil guide groove 13, and reduce the loss of coolant during the transportation process. That is, by increasing the height of the groove wall of the oil guide groove 13 in the vertical direction, the transportation efficiency and effect of the oil outlet pipe 112 on the coolant can be further improved, so as to further improve the working efficiency and life of the power assembly 1000.

[0173] Of course, the above-mentioned embodiments can be applied individually or in combination. The above is the preferred embodiment of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the principles of the present application. These improvements and modifications are also regarded as the scope of protection of the present application.

Claims

1. A power assembly with a combined fuel injection pipe, characterized in that: The power assembly includes a housing and a combined fuel injection pipe, wherein the housing is used to accommodate the reducer of the power assembly and to fix the fuel injection pipe, wherein the fuel injection pipe includes: An integrally formed oil delivery pipe, the oil delivery pipe comprising an oil inlet pipe and a plurality of oil outlet pipes, the plurality of oil outlet pipes being used to receive coolant through the oil inlet pipe, and each of the oil outlet pipes being used to output coolant to lubricate at least one of a gear or a bearing of the reducer; A combined nozzle, one end of the nozzle is used to be fixedly connected to one of the plurality of oil outlet pipes and to receive the coolant output by the oil outlet pipe, and the opening at the other end of the nozzle is used to output the coolant, wherein: The aperture of the opening at the one end of the one nozzle is larger than the aperture of the one oil outlet pipe, and larger than the aperture of the opening at the other end of the one nozzle.

2. The powertrain according to claim 1, characterized in that: Along the direction of coolant flow, the axis of the one nozzle coincides with the axis of the one oil outlet pipe, wherein: The oil outlet pipe is connected to the one end of the nozzle by welding.

3. The powertrain according to claim 1, characterized in that: The nozzle comprises a first annular protrusion, the first annular protrusion is located at one end of the nozzle along the direction of coolant flow, and the first annular protrusion is welded and fixed to the end surface of the oil outlet pipe facing the nozzle, wherein: The first annular protrusion is arranged around the periphery of the opening of the one end of the nozzle; Along the radial direction of the oil outlet pipe, the inner diameter of the first annular protrusion is larger than the inner diameter of the oil outlet pipe, and the outer diameter of the first annular protrusion is smaller than the outer diameter of the oil outlet pipe.

4. The powertrain according to claim 3, characterized in that: The one oil outlet pipe comprises a second annular protrusion, and along the direction of coolant flow, the one second annular protrusion is located on the end surface of the one oil outlet pipe facing the one nozzle, wherein: Along the radial direction of the oil outlet pipe, the inner diameter of the second annular protrusion is greater than or equal to the hole diameter of the oil outlet pipe, and the outer diameter of the second annular protrusion is less than or equal to the inner diameter of the first annular protrusion; Along the direction of coolant flow, an extension length of the second annular protrusion is less than or equal to an extension length of the first annular protrusion.

5. The powertrain according to claim 4, characterized in that: The one oil outlet pipe comprises another second annular protrusion, and along the radial direction of the one oil outlet pipe, the another second annular protrusion is arranged around the periphery of the one second annular protrusion, wherein: Along the radial direction of the one oil outlet pipe, the inner diameter of the other second annular protrusion is greater than or equal to the outer diameter of the one first annular protrusion; Along the direction of coolant flow, an extension length of the other second annular protrusion is less than or equal to an extension length of the one first annular protrusion and greater than an extension length of the one second annular protrusion.

6. The powertrain according to claim 5, characterized in that: Along the radial direction of the oil outlet pipe, the interval between the second annular protrusion and the other second annular protrusion is greater than the thickness of the first annular protrusion, wherein: The thickness of the one second annular protrusion is less than or equal to the thickness of the other second annular protrusion.

7. The powertrain according to claim 3, characterized in that: The one nozzle further comprises another first annular protrusion, and the another first annular protrusion is located on a side of the one nozzle away from the one first annular protrusion along the direction of flow of the coolant, wherein: The outer diameter of the other first annular protrusion is smaller than the outer diameter of the one first annular protrusion, and smaller than or equal to the inner diameter of the one first annular protrusion.

8. The powertrain according to claim 1, characterized in that: Along the direction of coolant flow, the nozzle comprises two connected sections, one section is used to receive the coolant delivered by the oil outlet pipe and to deliver it to the other section, the other section is used to output the coolant, wherein: Along the direction of coolant flow, the extension length of one of the sections is greater than the extension length of the other section; The aperture of one of the sections gradually decreases along the direction of coolant flow, and the aperture of the other section is smaller than or equal to the minimum aperture of one of the sections.

9. The powertrain according to claim 1, characterized in that: The one oil injection pipe also includes another nozzle, one end of which is used to be fixedly connected to another oil outlet pipe among the multiple oil outlet pipes and to receive the coolant delivered by the other oil outlet pipe, and the opening at the other end of the other nozzle is used to deliver the coolant to lubricate another gear or another bearing of the reducer, wherein: The other end of the other nozzle is flat-mouthed; Along the direction of coolant flow, the length dimension of the opening of the other end of the other nozzle is larger than the aperture of the other oil outlet pipe, and the width dimension of the opening of the other end of the other nozzle is smaller than the aperture of the other oil outlet pipe.

10. The powertrain according to claim 9, characterized in that: The opening of the other end of the other nozzle along the direction of coolant flow faces the other gear, wherein: Along the direction of coolant flow, a length direction of the opening of the other end of the other nozzle is parallel to the axial direction of the other gear.

11. The power assembly according to any one of claims 1 to 10, characterized in that: The extension direction of the one oil inlet pipe intersects with the extension direction of each oil outlet pipe; The aperture of the one oil inlet pipe is larger than the aperture of any of the multiple oil outlet pipes.

12. The power assembly according to any one of claims 1 to 10, characterized in that: Along the direction of coolant flow in the one oil inlet pipe, the multiple oil outlet pipes are spaced apart from each other, wherein: The interval between any two adjacent oil outlet pipes among the plurality of oil outlet pipes is greater than the aperture of any one of the two oil outlet pipes; The included angle between the extension direction of each of the oil outlet pipes and the direction of coolant flow in the one oil inlet pipe is less than or equal to 90°.

13. The power assembly according to any one of claims 1 to 10, characterized in that: The housing includes an oil delivery hole, and the oil delivery hole is used to deliver coolant to the plurality of oil outlet pipes through the oil inlet pipe, wherein: The one oil inlet pipe comprises an oil inlet port, and the one oil inlet port is used to receive the coolant delivered by the one oil delivery hole; Along the direction of coolant flow in the one oil inlet pipe, the one oil inlet port is located on the same side of the opening of each of the oil outlet pipes connected to the one oil inlet pipe.

14. The power assembly according to any one of claims 1 to 10, characterized in that: Along the direction of coolant flow in each of the oil outlet pipes, the interval between each of the oil outlet pipes and the one gear or the one bearing of the reducer is less than or equal to 30 mm.

15. A fuel injection pipe, characterized in that: The oil injection pipe includes an integrally formed oil delivery pipe and a plurality of assembled nozzles. The oil delivery pipe includes an oil inlet pipe and a plurality of oil outlet pipes. The oil inlet pipe is used to receive coolant and to deliver coolant to each of the oil outlet pipes. Each of the oil outlet pipes is used to deliver coolant to a gear or a bearing of the reducer for lubrication, wherein: One end of one of the plurality of nozzles is used to be fixedly connected to one of the plurality of oil outlet pipes by welding and is used to receive the coolant output by the one oil outlet pipe, and the aperture of the opening of the one end of the nozzle is larger than the aperture of the opening of the other end of the nozzle; One end of another one of the plurality of nozzles is used to be fixedly connected to another one of the plurality of oil outlet pipes by welding and is used to receive the coolant output by the another oil outlet pipe, and the opening of the other end of the another nozzle is flat; The one nozzle, the other nozzle and the remaining one of the multiple oil outlet pipes or the remaining multiple oil outlet pipes are respectively used to transport coolant to a gear or a bearing at a different position in the reducer for lubrication.

16. A vehicle, characterized in that: The vehicle comprises wheels and a powertrain as claimed in any one of claims 1 to 14 or comprises a fuel injection pipe as claimed in claim 15, wherein the powertrain is used to drive the wheels.

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