All-terrain vehicles and their engines

Abstract

The present invention discloses an all-terrain vehicle and its engine. The engine includes: a crankcase, which includes: a case body, a crankshaft, and a balance shaft. The crankshaft and the balance shaft are both arranged in the case body and driven by the crankshaft and the balance shaft; a water pump, which includes: a pump shaft, a sleeve, and an impeller. The axial first end of the pump shaft is fixedly connected to the balance shaft or the crankshaft, the sleeve is sleeved on the pump shaft, and the impeller is arranged at the axial second end of the pump shaft and stops against the sleeve so that the impeller, the sleeve, and the pump shaft rotate synchronously. Thus, the pump shaft is driven to rotate by the balance shaft, which can increase the speed of the pump shaft and further improve the water pumping capacity of the impeller. In this way, the water pump can reduce the size of the impeller accordingly while ensuring sufficient water pumping volume, thereby further reducing the volume of the water pump, which is beneficial to the miniaturization design goal of the engine. In addition, the sleeve can ensure the installation reliability of the impeller and improve the corrosion resistance of the pump shaft.

Description

Technical Field

[0001] The present invention relates to the technical field of all-terrain vehicles, in particular to an all-terrain vehicle and an engine thereof. Background Art

[0002] In a water-cooled engine, a water pump and an oil pump are generally installed on one side of the crankcase. The water pump is used for cooling water circulation, and the oil pump is used for lubricating oil circulation. The oil pump shaft and the water pump shaft are generally equipped with transmission wheels. The two transmission wheels are axially spaced and then driven by the transmission wheel of the crankshaft.

[0003] When the engine is idling, the oil pump shaft rotates at a low speed, which in turn causes the water pump shaft to rotate at a low speed. This prevents the water pump from functioning properly and prevents the cooling water from circulating properly in the engine's cooling water channels. This can lead to poor engine cooling and performance, and the water pump also takes up a large amount of space. Furthermore, as engine speed and performance increase, the performance requirements for the water pump are becoming increasingly stringent, particularly with regard to sealing performance and cost requirements at high speeds. This type of transmission is no longer sufficient for water pumps. Summary of the Invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, one object of the present invention is to provide an engine for an all-terrain vehicle that can increase the speed of a water pump, thereby improving the water pumping capacity, and improving the corrosion resistance of the pump shaft, thereby reducing the size and cost of the water pump.

[0005] The present invention further provides an all-terrain vehicle.

[0006] According to the engine of the all-terrain vehicle of the present invention, it includes: a crankcase, which includes: a case body, a crankshaft and a balance shaft, the crankshaft and the balance shaft are both arranged in the case body, and the crankshaft and the balance shaft are driven; a water pump, which includes: a pump shaft, a sleeve and an impeller, the axial first end of the pump shaft is fixedly connected to the balance shaft or the crankshaft, the sleeve is sleeved on the pump shaft, and the impeller is arranged at the axial second end of the pump shaft and stops against the sleeve, so that the impeller, the sleeve and the pump shaft rotate synchronously.

[0007] Therefore, by driving the pump shaft to rotate through the balance shaft, the rotation speed of the pump shaft can be increased, and the water pumping capacity of the impeller can be further improved. In this way, the water pump can reduce the size of the impeller accordingly on the basis of ensuring sufficient water pumping volume, thereby further reducing the volume of the water pump, which can be beneficial to the miniaturization design goal of the engine. In addition, the setting of the shaft sleeve can ensure the installation reliability of the impeller and facilitate the contact between other components and the pump shaft.

[0008] In some examples of the present invention, the axial first end of the pump shaft is fixedly connected to the balance shaft, the axial first end of the balance shaft is provided with an axially extending groove, and the axial first end of the pump shaft is provided with an axially extending protrusion, and the protrusion fits in the groove.

[0009] In some examples of the present invention, the protrusion is loosely fitted into the groove.

[0010] In some examples of the present invention, the protrusion is a non-circular protrusion, and the groove is a non-circular groove.

[0011] In some examples of the present invention, the protrusion is in the shape of a flat block with a rectangular cross section, and the groove is in the shape of a flat square groove with a rectangular cross section.

[0012] In some examples of the present invention, both ends of the groove in the width direction are open, and both ends of the protrusion in the width direction extend out of both ends of the groove.

[0013] In some examples of the present invention, the outer circumferential surface of the pump shaft is provided with a circumferentially extending receiving groove, a sealing ring is provided in the receiving groove, and the sealing ring abuts against the inner circumferential surface of the shaft sleeve.

[0014] In some examples of the present invention, the pump shaft includes: a first shaft segment and a second shaft segment, the first shaft segment and the second shaft segment are connected, the outer diameter of the first shaft segment is larger than the outer diameter of the second shaft segment and a step is formed at the connection between the first shaft segment and the second shaft segment, and the shaft sleeve and the impeller sleeve are arranged on the second shaft segment.

[0015] In some examples of the present invention, a first washer is provided at the step, and the shaft sleeve is stopped on the first washer.

[0016] In some examples of the present invention, a second washer and a fastener are provided at the second axial end of the pump shaft, the fastener passes through the second washer to fix the impeller to the second axial end of the pump shaft, and the second washer is located axially outside the impeller.

[0017] In some examples of the present invention, a box cover is fixed to one side of the box body, and the box cover is integrally formed with a pump casing of the water pump. The pump casing is provided with an axially extending through hole, and the pump shaft is passed through the through hole.

[0018] In some examples of the present invention, the engine further includes: an oil seal, the oil seal sleeve being disposed on the shaft sleeve and also abutting against the inner circumferential wall of the through hole, and the shaft sleeve being rotatable relative to the oil seal.

[0019] In some examples of the present invention, there are two oil seals, and the two oil seals are spaced apart in the axial direction.

[0020] In some examples of the present invention, the engine further includes: a generator fixed to the second axial side of the crankcase, the generator including a rotor shaft connected to the crankshaft with axes thereof being colinear.

[0021] The all-terrain vehicle according to the present invention comprises the engine of the all-terrain vehicle.

[0022] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the following description of the embodiments with reference to the accompanying drawings, in which:

[0024] Figure 1 is a perspective view of an engine according to an embodiment of the present invention;

[0025] Figure 2 is a side view of an engine according to an embodiment of the present invention;

[0026] Figure 3 It is along Figure 2 Cross-sectional view in the AA direction;

[0027] Figure 4 yes Figure 3 Enlarged view in middle area B;

[0028] Figure 5 is a perspective view of an engine according to an embodiment of the present invention, exploded at the sealing cover;

[0029] Figure 6 This is an exploded view of the sealing cover and the second connecting pipe;

[0030] Figure 7 This is an exploded view of the tank cover and pump cover;

[0031] Figure 8 It is a three-dimensional picture of the box lid;

[0032] Figure 9 This is an exploded view of the balance shaft and pump shaft.

[0033] Reference numerals:

[0034] Engine 1000;

[0035] Crankcase 100; case body 110; second joint surface 110b; case cover 111; pump housing 112; through hole 113; large hole section 113a; small hole section 113b; impeller chamber 114; sealing cover 115; recess 116; water port 117; second cooling channel 118; cylinder water inlet port 119;

[0036] Crankshaft 120; balance shaft 130; groove 131; pump cover 140; water pump inlet port 141; cylinder return port 142; oil cooler return port 143;

[0037] Water pump 200; pump shaft 210; bump 211; first shaft section 212; second shaft section 213;

[0038] Shaft sleeve 220; impeller 230; sealing ring 240; first gasket 250; second gasket 260; fastener 270; oil seal 280;

[0039] Generator 300; oil cooler 400; oil cooler water inlet pipe 410; oil cooler water return pipe 420;

[0040] Cylinder 500; exhaust port 510; cylinder water inlet pipe 600; first connecting pipe 610; second connecting pipe 620. DETAILED DESCRIPTION

[0041] The embodiments of the present invention will be described in detail below. The embodiments described with reference to the accompanying drawings are exemplary. The embodiments of the present invention will be described in detail below.

[0042] Reference below Figures 1-9 An engine 1000 according to an embodiment of the present invention is described, and the engine 1000 is applied to an all-terrain vehicle.

[0043] like Figure 1 and Figure 2 As shown, the engine 1000 according to an embodiment of the present invention may include: a crankcase 100, a cylinder 500 and a water pump 200, the cylinder 500 is installed above the crankcase 100, and the water pump 200 is installed on one axial side of the crankcase 100, and the axial side is the left and right side. For example, the water pump 200 can be installed on the left side of the crankcase 100, wherein the right side of the crankcase 100 can be adjusted and arranged according to the power type of the all-terrain vehicle. For example, if the all-terrain vehicle is a hybrid all-terrain vehicle, a generator 300 can be provided on the right side of the crankcase 100, and the generator 300 can be electrically connected to the electric motor, and the electric motor outputs power to drive the all-terrain vehicle to move; for another example, if the all-terrain vehicle is a pure fuel all-terrain vehicle, a gearbox can be provided on the right side of the crankcase 100.

[0044] like Figure 3As shown, a plurality of transmission components may be arranged in the crankcase 100, including: a case body 110, a case cover 111, a crankshaft 120 and a balance shaft 130. The crankshaft 120 and the balance shaft 130 are both arranged in the case body 110. The case cover 111 is fixed to one side of the case body 110. A piston is arranged in the cylinder 500. The piston rod and the connecting rod connect the piston and the crankshaft 120. In this way, the reciprocating motion of the piston can be converted into the rotation of the crankshaft 120. The crankshaft 120 and the balance shaft 130 are driven. The balance shaft 130 can effectively smooth the vibration of the engine 1000 and improve the performance of the engine 1000.

[0045] like Figure 3 As shown, water pump 200 includes a pump shaft 210, a sleeve 220, and an impeller 230. The first axial end of pump shaft 210 is fixedly connected to balance shaft 130 or crankshaft 120, i.e., the right end of pump shaft 210 is fixedly connected to the left end of balance shaft 130. Sleeve 220 is mounted on pump shaft 210, and impeller 230 is disposed at the second axial end of pump shaft 210, i.e., the left end of pump shaft 210. Furthermore, impeller 230 abuts sleeve 220, allowing the impeller 230, sleeve 220, and pump shaft 210 to rotate synchronously. In other words, sleeve 220 is mounted on pump shaft 210 and then abuts against impeller 230, allowing the pump shaft 210, impeller 230, and sleeve 220 to rotate synchronously. Impeller 230 stirs the cooling water around it, thereby supplying the cooling water to the corresponding components to be cooled.

[0046] Therefore, by driving the pump shaft 210 to rotate through the balance shaft 130 or the crankshaft 120, the rotation speed of the pump shaft 210 can be increased, and the water pumping capacity of the impeller 230 can be further improved. In this way, the water pump 200 can reduce the size of the impeller 230 accordingly on the basis of ensuring sufficient water pumping volume, thereby further reducing the volume of the water pump 200, which can be beneficial to the miniaturization design goal of the engine 1000. In addition, the setting of the shaft sleeve 220 can ensure the installation reliability of the impeller 230, improve the corrosion resistance of the pump shaft 210, and facilitate the contact between other components and the pump shaft 210.

[0047] According to an optional embodiment of the present invention, Figure 4As shown, the axial first end of the pump shaft 210 is fixedly connected to the balance shaft 130, and the axial end of the balance shaft 130 is provided with an axially extending groove 131. The axial first end (i.e., the right end) of the pump shaft 210 is provided with an axially extending protrusion 211. The protrusion 211 fits in the groove 131, and the protrusion 211 and the groove 131 are circumferentially limited. The matching method of the groove 131 and the protrusion 211 is simple and reliable, and can effectively perform circumferential limitation, which can ensure the transmission stability of the balance shaft 130 and the pump shaft 210. Among them, the protrusion 211 can be a sheet structure with a certain thickness, and the groove 131 can also be a long strip groove with a certain thickness. This can effectively ensure the circumferential limitation of the protrusion 211 and the groove 131.

[0048] The projection 211 and the groove 131 can be clearance-fitted. The clearance-fitting facilitates assembly and avoids the occurrence of jamming caused by misalignment between the pump shaft 21 and the balance shaft 130 due to machining errors, thereby increasing transmission stability.

[0049] Among them, Figure 9 As shown, the protrusion 211 is a non-circular protrusion 211, and the groove 131 is a non-circular groove 131. The protrusion 211 and the groove 131 set in this way can utilize the protruding part of the protrusion 211 to cooperate with the part of the groove 131, so that the balance shaft 130 and the pump shaft 210 can rotate synchronously, and can also ensure that the two are coaxially arranged.

[0050] Further, if Figure 9 As shown, the protrusion 211 is flat and block-shaped, with a rectangular cross-section, while the groove 131 is a flat square groove with a rectangular cross-section. This arrangement of the protrusion 211 and groove 131 provides a simple structure and facilitates alignment during assembly. It also ensures the structural reliability of the pump shaft 210 and the balance shaft 130, further improving the reliability of their fit.

[0051] Also, such as Figure 9 As shown, both ends of the groove 131 in the width direction are open, and both ends of the protrusion 211 in the width direction extend beyond the ends of the groove 131. In other words, the length of the protrusion 211 in the width direction is greater than the length of the groove 131 in the width direction. This arrangement of the protrusion 211 and the groove 131 provides a stable fit, and the structural strength of the protrusion 211 is high, which can prevent the protrusion 211 from deforming during transmission.

[0052] Further, if Figure 4As shown, the outer circumferential surface of the pump shaft 210 is provided with a circumferentially extending receiving groove, i.e., the receiving groove is annular. A sealing ring 240 is disposed within the receiving groove, and the sealing ring 240 abuts against the inner circumferential surface of the shaft sleeve 220. In other words, the sealing ring 240 is disposed between the pump shaft 210 and the shaft sleeve 220. The provision of the sealing ring 240 effectively seals the gap between the pump shaft 210 and the shaft sleeve 220, effectively separating the inner cavity of the water pump 200 from the inner cavity of the crankcase 100, thereby improving the reliability of the engine 1000.

[0053] Among them, Figure 4 As shown, the pump shaft 210 includes a first shaft segment 212 and a second shaft segment 213. The first shaft segment 212 and the second shaft segment 213 are connected. The outer diameters of the first shaft segment 212 and the second shaft segment 213 are different, with the outer diameter of the first shaft segment 212 being larger than that of the second shaft segment 213. A step is formed at the connection between the first and second shaft segments 212 and 213, and the sleeve 220 and the impeller 230 are sleeved on the second shaft segment 213. The step thus limits the axial position of the sleeve 220 and the impeller 230, preventing them from axial movement to at least a certain extent. Furthermore, the pump shaft 210 thus configured also facilitates the sleeve installation of the sleeve 220.

[0054] Further, if Figure 4 As shown, a first washer 250 is provided at the step, and the shaft sleeve 220 abuts against the first washer 250. The first washer 250 acts as a buffer between the shaft sleeve 220 and the step, preventing the shaft sleeve 220 from directly impacting the step of the pump shaft 210 during axial movement, thereby ensuring the structural reliability of the water pump 200. Furthermore, the first washer 250 can be attached to the inner sidewall of the pump housing 112 of the water pump 200, providing at least a certain degree of sealing.

[0055] Alternatively, as Figure 4 As shown, a second washer 260 and a fastener 270 are provided at the second axial end of the pump shaft 210. The fastener 270 passes through the second washer 260 to secure the impeller 230 to the second axial end of the pump shaft 210. The second washer 260 abuts against the impeller 230 and is located axially outward of the impeller 230. It will be appreciated that a threaded hole is provided at the end of the second shaft section 213 of the pump shaft 210. The fastener 270 can be a bolt that passes through the second washer 260 and extends into the threaded hole. In this way, the fastener 270 secures the impeller 230 and the sleeve 220 to the second shaft section 213, allowing the impeller 230 and the sleeve 220 to rotate synchronously with the second shaft section 213, thereby ensuring the pumping capacity of the impeller 230. The second washer 260 prevents direct contact between the impeller 230 and the fastener 270, effectively protecting the impeller 230.

[0056] Combine Figure 3 and Figure 4 As shown, the case cover 111 is integrally formed with a pump casing 112 of the water pump 200, and the pump casing 112 is provided with an axially extending through hole 113, and the pump shaft 210 is passed through the through hole 113. By integrally forming the pump casing 112 on the case cover 111, the process of setting and installing the pump casing 112 can be omitted, and the crankcase 100 and the water pump 200 can be made structurally reliable. The through hole 113 can facilitate the pump shaft 210 to pass through and connect with the balance shaft 130. By reasonably setting the inner diameter of the through hole 113, the cooling water can also be prevented from entering the internal space of the case body 110 to at least a certain extent. It should be noted that the axial first end of the pump shaft 210 can also be directly driven by the crankshaft 120, instead of the way it is driven by the balance shaft 130.

[0057] According to a specific embodiment of the present invention, Figure 4 As shown, the engine 1000 may also include: an oil seal 280, which is sleeved on the shaft sleeve 220, and the shaft sleeve 220 can rotate relative to the oil seal 280, and the outer periphery of the oil seal 280 also abuts against the inner peripheral wall of the through hole 113. The pump housing 112 also forms an impeller cavity 114 around the impeller 230, and there is flowing cooling water in the impeller cavity 114. The impeller 230 can pump the cooling water in the impeller cavity 114 into the position of the component to be cooled through the interface. The oil seal 280 can play a sealing role, and it can also replace the water seal to isolate the impeller cavity 114 from the internal space of the housing 110. Moreover, the oil seal 280 is more suitable for working at high speeds than the water seal, which can make the sealing effect of the water pump 200 better. In addition, the cost of the oil seal 280 is relatively low.

[0058] Specifically, if Figure 4 As shown, there are two oil seals 280, spaced axially apart. Providing two oil seals 280 can improve the sealing performance of the water pump 200 to at least a certain extent, making the engine 1000 more reliable and stable. The two oil seals 280 can have different outer diameters. For example, the outer diameter of the oil seal 280 closer to the impeller 230 can be larger than the outer diameter of the oil seal 280 farther from the impeller 230. This allows for better adaptation to the size of the hole 113 and provides a more secure seal for the water pump 200.

[0059] Specifically, if Figure 4As shown, the through hole 113 includes: a large hole section 113a and a small hole section 113b, the small hole section 113b is located on the inner side of the large hole section 113a, and the small hole section 113b corresponds to the first shaft section 212 of the pump shaft 210, wherein the small hole section 113b and the first shaft section 212 of the pump shaft 210 are clearance-matched, so that the first shaft section 212 of the pump shaft 210 can rotate freely in the small hole section 113b, and the large hole section 113a corresponds to the second shaft section 212 of the pump shaft 210. 3. In this way, radially, there is a certain amount of space between the inner circumferential wall of the large bore section 113a and the outer circumferential surface of the second shaft section 213 of the pump shaft 210, facilitating the placement of sealing components. For example, an oil seal 280 is disposed within the large bore section 113a. Two oil seals 280 are spaced apart in the axial direction of the large bore section 113a. For example, the two oil seals 280 are positioned adjacent to the axial ends of the large bore section 113a, and the oil seals 280 abut against the inner circumferential wall of the large bore section 113a. It is understood that by properly arranging the large bore section 113a and the second shaft section 213 of the pump shaft 210, the placement of the oil seals 280 can be facilitated. The oil seals 280 can isolate the impeller chamber 114 from the interior space of the casing 110 at the junction between the two, preventing moisture in the impeller chamber 114 from entering the interior of the casing 110, thereby ensuring the sealing reliability of the engine 1000.

[0060] Furthermore, the inner circumferential wall of the large bore section 113a is provided with an outer step and an inner step. One of the two oil seals 280 abuts against the outer step, while the other of the two oil seals 280 abuts against the inner step. The provision of the outer and inner steps effectively improves the positional reliability of the two oil seals 280 within the large bore section 113a, further enhancing the sealing effect of the oil seals 280 and ensuring the sealing reliability of the engine 1000.

[0061] According to an optional embodiment of the present invention, Figure 1 and Figure 4 As shown, an oil cooler 400 is disposed outside the housing 110. The pump housing 112 further defines an impeller cavity 114 outside the through-hole 113. The impeller cavity 114 is connected to an oil cooler water inlet pipe 410. The oil cooler 400 cools the oil in certain components of the engine 1000. The pump housing 112 is provided with an interface for connecting to the oil cooler water inlet pipe 410. By forming the impeller cavity 114 within the pump housing 112, the placement of the impeller 230 and the connection of the oil cooler water inlet pipe 410 are facilitated. Among them, the oil cooler 400 is arranged on the front side or the rear side of the crankcase 100, and an oil cooler return pipe 420 is also connected between the water pump 200 and the oil cooler 400. The cold water in the impeller chamber 114 enters the oil cooler 400 through the oil cooler inlet pipe 410, fully exchanges heat with the lubricating oil, reduces the temperature of the lubricating oil, and finally returns to the impeller chamber 114 of the water pump 200 through the oil cooler return pipe 420.

[0062] Among them, Figure 1 As shown, the pump housing 112 is located at the edge of the tank cover 111. The pump housing 112 is arranged in a reasonable position, which can reduce the manufacturing difficulty of the tank cover 111, and can match the pump shaft 210 and the impeller 230.

[0063] Alternatively, as Figure 1 As shown, a cylinder water inlet pipe 600 is connected between the impeller chamber 114 and the cylinder 500. The interface connecting the impeller chamber 114 to the cylinder water inlet pipe 600 is arranged obliquely above the impeller chamber 114, that is, the interface is arranged obliquely above the position of the pump housing 112 corresponding to the impeller chamber 114. By providing the cylinder water inlet pipe 600, the impeller chamber 114 can supply cooling water to the cylinder 500, thereby effectively reducing the operating temperature of the cylinder 500 when the engine 1000 is working, and allowing the engine 1000 to be in a reasonable operating temperature range. In addition, by arranging the interface obliquely above the impeller chamber 114, the connection between the cylinder 500 and the impeller chamber 114 can be facilitated, and the length of the cylinder water inlet pipe 600 can be reduced, which can further simplify the difficulty of arranging the cylinder water inlet pipe 600.

[0064] According to a specific embodiment of the present invention, Figure 1 and Figure 4 As shown, the casing cover 111 is recessed toward the interior space to form the pump casing 112, and a pump cover 140 is fixed to the outside of the pump casing 112. By recessing the casing 112 toward the interior, a pump casing 112 with sufficient space can be formed at the casing cover 111. The pump casing 112 can accommodate the impeller 230 and the pump shaft 210. The outer pump cover 140 can effectively seal the space of the pump casing 112, thereby ensuring the sealing of the water pump 200.

[0065] Among them, Figure 8 As shown, the casing cover 111 is provided with an annular edge extending outwardly around the outer periphery of the through hole 113. The annular edge defines an impeller cavity 114, and at least a portion of the impeller 230 is accommodated in the impeller cavity 114. In other words, the casing cover 111 can extend an annular edge from its outer surface surrounding the through hole 113, and the annular edge can define an impeller cavity 114 for accommodating the impeller 230. The pump casing 112 configured in this manner has a simple structure, which can reduce the difficulty of molding the casing cover 111 and effectively accommodate the impeller 230.

[0066] Also, such as Figure 8As shown, the casing cover 111 is further provided with a cylinder water inlet port 119 on one side of the annular edge, and the cylinder water inlet port 119 is in communication with the impeller chamber 114. In other words, the casing cover 111 is not only integrally formed with the pump casing 112, but also integrally formed with the cylinder water inlet port 119. This eliminates the need to further provide the cylinder water inlet port 119 on the pump casing 112, thereby further simplifying the structure of the engine 1000 and making the water pump 200 more reliable.

[0067] Specifically, if Figure 1 As shown, the pump cover 140 is provided with a water pump inlet interface 141, a cylinder return water interface 142 and an oil cooler return water interface 143. The water pump inlet interface 141, the cylinder return water interface 142 and the oil cooler return water interface 143 are connected. The pump cover 140 is also provided with reinforcing ribs, which extend from the edge of the pump cover 140 to the connection between the water pump inlet interface 141, the cylinder return water interface 142 and the oil cooler return water interface 143. As a result, the pump cover 140 integrates three interfaces, and the cooling water at these three interfaces can enter the impeller chamber 114 and then supply the corresponding components for cooling. The provision of the reinforcing ribs can improve the reliability of the pump cover 140 and the reliability of the three interfaces in the pump cover 140, thereby further improving the reliability of the engine 1000.

[0068] Optionally, a sight glass is provided on the pump housing 112. One end of the sight glass communicates with the impeller chamber 114, and the other end is sealed. The sight glass is a transparent tube that allows the user to directly see the cooling water inside. This facilitates monitoring the water quality within the water pump 200, thereby providing information on the water quality of the entire circulation loop and allowing the user to replace the cooling water in a timely manner, thereby ensuring the operational stability of the engine 1000.

[0069] The structure and process of the water pump 200 supplying cooling water to the cylinder 500 will be described in detail below with reference to the accompanying drawings.

[0070] like Figure 1 As shown, the cylinder 500 is provided with an exhaust port 510 and a first cooling channel (not shown). The exhaust port 510 is used to discharge gas and is connected to an exhaust pipe. Cooling water flows in the first cooling channel. A cylinder hole is formed in the cylinder 500 and the first cooling channel is provided around the cylinder hole. The top of the crankcase 100 is spaced a predetermined distance from the exhaust port 510, i.e. Figure 1 As shown, the top of the crankcase 100 is spaced a certain distance from the exhaust port 510 in the vertical direction, and thus a certain distance is also spaced from the exhaust pipe.

[0071] One end of the cylinder water inlet pipe 600 is connected to the water pump 200, and the cylinder water inlet pipe 600 is attached and fixed to the crankcase 100. The other end of the cylinder water inlet pipe 600 is connected to the first cooling channel. The cylinder water inlet pipe 600 is attached and fixed to the crankcase 100, which can further effectively separate the cylinder water inlet pipe 600 and the exhaust pipe, effectively increasing the distance between the two, thereby preventing the high-temperature exhaust pipe from affecting the low-temperature cylinder water inlet pipe 600, further improving the cooling effect of the engine 1000, and thus ensuring the working reliability of the engine 1000 and improving the fuel efficiency of the engine 1000. There is no need for the effective distance between the water inlet pipe and the crankcase as in the prior art, coupled with space limitations, so it is easy to approach the exhaust pipe.

[0072] Specifically, the crankcase 100 includes a second cooling channel 118, which is connected to the first cooling channel. That is, cooling water flows between the second cooling channel 118 and the first cooling channel, and the cooling water in the second cooling channel 118 can be supplied to the first cooling channel. In other words, the cylinder water inlet pipe 600 is not directly connected to the first cooling channel, but rather is connected through the second cooling channel 118. The cooling water pumped from the water pump 200 needs to pass through the cylinder water inlet pipe 600 and the second cooling channel 118 in sequence before entering the first cooling channel for cooling. The cooling water in the first cooling channel can also flow back to the water pump 200.

[0073] Therefore, the cylinder water inlet pipe 600 does not need to contact the cylinder 500, and it can transfer cooling water through the second cooling channel 118, that is, it can be separated by the second cooling channel 118, reducing the impact of high-temperature exhaust gas on the water inlet pipe, and can further improve the cooling effect of the engine 1000, thereby ensuring the working reliability of the engine 1000 and improving the fuel efficiency of the engine 1000.

[0074] Alternatively, as Figure 1 As shown, the cylinder water inlet pipe 600 includes a first connecting pipe 610 and a second connecting pipe 620. The first connecting pipe 610 is bent, with its ends connected to the water pump 200 and one end of the second connecting pipe 620, respectively. The second connecting pipe 620 is attached to the outer surface of the crankcase 100 and extends at an angle. The bending of the first connecting pipe 610 changes its direction, allowing it to be effectively connected between the water pump 200 and the second connecting pipe 620. This also facilitates the attachment and fixation of the second connecting pipe 620 to the surface of the crankcase 100, thereby better away from the exhaust pipe and improving the cooling effect of the cooling water on the engine 1000. The tilted second connecting pipe 620 also further reduces its extended length, allowing for better connection to the second cooling channel 118.

[0075] Among them, Figure 1 As shown, the wall of the second connecting pipe 620 is provided with an opening, which is sealed by the crankcase 100. In other words, the second connecting pipe 620 has an opening that opens toward the crankcase 100, which is sealed by the crankcase 100. Specifically, the second connecting pipe 620 is open not only at both ends but also on the side facing the crankcase 100. The two ends are primarily used to connect to the first connecting pipe 610 and the second cooling channel 118. The side facing the crankcase 100 is open, facilitating its secure connection to the top of the crankcase 100 and making it flatter, further away from the exhaust pipe and thus reducing the temperature of the cylinder 500. A sealing gasket is provided between the open side of the second connecting pipe 620 facing the top of the crankcase 100 and the top of the crankcase 100. This gasket effectively seals the gap between the two and prevents coolant leakage. The sealing gasket is a rubber gasket. Of course, the second connecting pipe 620 can also be arranged in other ways. For example, a sealed bottom wall can be provided on the side of the second connecting pipe 620 facing the crankcase 100. The sealed bottom wall has a bottom plane and can be flatly attached to the top wall of the crankcase 100.

[0076] Specifically, the first connecting tube 610 may be a rubber tube, and the second connecting tube 620 may be an aluminum alloy tube. Rubber tubes are easily deformable and can be bent, effectively connecting the impeller chamber 114 of the water pump 200 and the second connecting tube 620. The second connecting tube 620, located near the exhaust port 510, is constructed from an aluminum alloy tube. Aluminum alloy tubes offer superior structural strength and are less susceptible to deformation at high temperatures, unlike rubber tubes, which can be affected by the exhaust pipe's temperature. Furthermore, aluminum alloy tubes can be more easily attached to and secured to the top of the crankcase 100.

[0077] Alternatively, as Figure 1 As shown, the crankcase 100 includes a case 110 and a sealing cover 115. The sealing cover 115 is disposed at the top of the case 110 and spaced apart from the cylinder 500. The second connecting pipe 620 is attached and fixed to the sealing cover 115. The sealing cover 115 can be fixed to the case 110 via fasteners 270. Of course, the cylinder 500 is fixed directly above the case 110, and the sealing cover 115 can be disposed obliquely above the case 110. Furthermore, the provision of the sealing cover 115 further simplifies the placement of the second connecting pipe 620 in the crankcase 100, making it easier to place and secure the second connecting pipe 620 to the sealing cover 115.

[0078] The sealing cover 115 can be an aluminum alloy cover. Thus, the sealing cover 115 and the second connecting pipe 620 are made of the same material. The aluminum alloy material has high structural strength and good heat dissipation effect. This arrangement can further facilitate the heat dissipation of the cooling water and improve the cooling effect of the engine 1000.

[0079] Alternatively, as Figure 5 and Figure 6 As shown, the sealing cover 115 is provided with a recess 116 corresponding to the opening. The recess 116 can further expand the size of the second connecting pipe 620, while also reducing the height of the second connecting pipe 620 protruding from the crankcase to a certain extent, allowing a larger amount of cooling water to flow between the second connecting pipe 620 and the recess 116. Moreover, the provision of the recess 116 can at least to a certain extent reduce the height of the second connecting pipe 620, further away from the exhaust pipe.

[0080] Further, if Figure 5 and Figure 6 As shown, the sealing cover 115 is provided with a water port 117, which is connected between the second connecting pipe 620 and the second cooling channel 118. As a result, the connection structure between the second connecting pipe 620 and the second cooling channel 118 can be further simplified, and the cooling water can flow between the two. Figure 5 As shown, the housing 110 has a first joint surface and a second joint surface 110b. The first joint surface is connected to the cylinder 500, and the second joint surface 110b is connected to the sealing cover 115. The water inlet of the second cooling channel 118 is formed on the second joint surface 110b, and the water outlet is formed on the first joint surface. The water inlet is set on the side of the second joint surface 110b adjacent to the first joint surface. The second cooling channel 118 is smaller in size, which can reduce the space it occupies in the housing 110 and shorten the communication path between it and the first cooling channel, making the water channel layout more reasonable.

[0081] The end of the first connecting tube 610 is sleeved onto the end of the second connecting tube 620, and a clamp is provided on the end of the first connecting tube 610. This sleeve connection facilitates installation and ensures a tight connection between the first connecting tube 610 and the second connecting tube 620. The provision of the clamp also ensures a secure fixation between the ends of the first connecting tube 610 and the second connecting tube 620.

[0082] Among them, Figure 3 As shown, engine 1000 may further include a generator 300, which is fixed to the second axial side of crankcase 100. Generator 300 includes a rotor shaft, which is connected to crankshaft 120 with their axes collinear. It will be appreciated that when engine 1000 is operating, crankshaft 120 rotates, causing the rotor shaft to rotate accordingly, thereby generating electricity. Generator 300 may be connected to a power battery and an electric motor. The electricity generated by generator 300 can be directly supplied to the electric motor, thereby achieving hybrid operation and reducing fuel consumption of the all-terrain vehicle.

[0083] The all-terrain vehicle according to the embodiment of the present invention includes the engine 1000 of the all-terrain vehicle of the above embodiment.

[0084] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0085] In the description of the present invention, "first feature" and "second feature" may include one or more of the features. In the description of the present invention, "plurality" means two or more. In the description of the present invention, a first feature "above" or "below" a second feature may include the first and second features being in direct contact, or may also include the first and second features not being in direct contact but being in contact via another feature between them. In the description of the present invention, a first feature being "above", "above" and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is at a higher level than the second feature.

[0086] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "example," "specific example," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with the embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative expressions of the above terms do not necessarily refer to the same embodiment or example.

[0087] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. An engine for an all-terrain vehicle, characterized in that: include: The crankcase comprises a crankshaft, a balancing shaft, and a housing. The crankshaft and the balancing shaft are both disposed in the housing. The crankshaft and the balancing shaft are used for transmission. A housing cover is fixed to one side of the housing. A water pump, wherein the box cover is integrally formed with a pump casing of the water pump, the water pump comprising: a pump shaft, a shaft sleeve and an impeller, the shaft sleeve being sleeved on the pump shaft, the impeller being arranged at the second axial end of the pump shaft and abutting against the shaft sleeve so that the impeller, the shaft sleeve and the pump shaft rotate synchronously, the axial first end of the pump shaft is fixedly connected to the balance shaft, the axial first end of the balance shaft is provided with an axially extending groove, the axial first end of the pump shaft is provided with an axially extending protrusion, the protrusion is fitted in the groove, the protrusion and the groove are clearance-fitted, the pump casing forms an impeller cavity around the impeller, cooling water flows in the impeller cavity; The cylinder is installed above the crankcase, a cylinder water inlet pipe is connected between the cylinder and the impeller chamber, and the interface of the impeller chamber connected to the cylinder water inlet pipe is arranged obliquely above the impeller chamber.

2. The engine for an all-terrain vehicle according to claim 1, characterized in that The protrusion is a non-circular protrusion, and the groove is a non-circular groove.

3. The engine for an all-terrain vehicle according to claim 2, wherein: The protrusion is in the shape of a flat block with a rectangular cross section, the groove is in the shape of a flat square groove with a rectangular cross section and open at both ends, and the two ends of the protrusion in the width direction extend out of the two ends of the groove.

4. The engine for an all-terrain vehicle according to claim 1, wherein: The outer peripheral surface of the pump shaft is provided with a circumferentially extending receiving groove, a sealing ring is provided in the receiving groove, and the sealing ring abuts against the inner peripheral surface of the shaft sleeve.

5. The engine for an all-terrain vehicle according to claim 1, wherein: The pump shaft includes: a first shaft segment and a second shaft segment, the first shaft segment and the second shaft segment are connected, the outer diameter of the first shaft segment is larger than the outer diameter of the second shaft segment, and a step is formed at the connection between the first shaft segment and the second shaft segment, and the shaft sleeve and the impeller are sleeved on the second shaft segment.

6. The engine for an all-terrain vehicle according to claim 5, characterized in that: A first washer is provided at the step, and the shaft sleeve is stopped on the first washer.

7. The engine for an all-terrain vehicle according to claim 5, characterized in that: A second washer and a fastener are provided at the second axial end of the pump shaft. The fastener passes through the second washer to fix the impeller to the second axial end of the pump shaft. The second washer is located axially outside the impeller.

8. The engine for an all-terrain vehicle according to claim 1, wherein: The pump housing is provided with an axially extending through hole, and the pump shaft is passed through the through hole.

9. The engine for an all-terrain vehicle according to claim 8, characterized in that Also includes: An oil seal is provided on the shaft sleeve and is also in contact with the inner peripheral wall of the through hole. The shaft sleeve is rotatable relative to the oil seal.

10. The engine for an all-terrain vehicle according to claim 9, characterized in that There are two oil seals, and the two oil seals are spaced apart in the axial direction.

11. The engine for an all-terrain vehicle according to claim 1, wherein: Also includes: A generator is fixed on the second axial side of the crankcase. The generator includes a rotor shaft connected to the crankshaft with axes thereof being colinear.

12. An all-terrain vehicle, characterized in that: An engine for an all-terrain vehicle comprising any one of claims 1-11.

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