Power assembly

Abstract

The invention discloses a power assembly. The power assembly comprises an air cylinder cover, an air cylinder body, an air filter, an air inlet and exhaust mechanism, an air inlet valve body and a valve body connector. An air inlet channel is formed in the air cylinder cover. The air cylinder body is connected with the air cylinder cover and forms a combustion chamber. The air inlet channel communicates with the combustion chamber. The air filter is communicated with the air inlet channel; the air inlet and exhaust mechanism comprises an air inlet valve body communicated with the air filter; the air inlet valve body is connected to the air inlet channel through the valve body connector. The air inlet channel comprises air inlet holes, in the width direction of the power assembly, the maximum distance between the two farthest air inlet holes is set to be a first length, the maximum length of the air inlet valve body in the width direction of the power assembly is set to be a second length, and the ratio of the first length to the second length is larger than 0.66 and smaller than or equal to 0.96. Through the arrangement, the distance between the air inlets is reduced, so that the structure between the air inlets is more compact, and the structural compactness of the cylinder cover is improved.

Description

Technical Field

[0001] The present invention relates to the technical field of power devices, in particular to a power assembly. Background Art

[0002] In the prior art, the power assembly includes a cylinder head, and an intake passage is formed in the cylinder head, and external gas enters the cylinder head through the intake passage. Generally speaking, the intake passage includes intake holes connected to the outside, and the intake holes are arranged horizontally along the width direction of the cylinder head. Since the distance between the intake holes is large, the structure of the cylinder head is not compact, which in turn causes the structure of the power assembly to be not compact. Summary of the invention

[0003] In order to solve the deficiencies of the prior art, an object of the present invention is to provide a power assembly with a compact structure.

[0004] To achieve the above object, the present invention adopts the following technical solution:

[0005] A powertrain includes a cylinder head, a cylinder block, an air filter, and an intake and exhaust mechanism. An intake duct is formed in the cylinder head; the cylinder block is connected to the cylinder head and forms a combustion chamber, and the intake duct is communicated with the combustion chamber; the air filter is communicated with the intake duct; the intake and exhaust mechanism includes an intake valve body and a valve body connector, and the intake valve body is communicated with the air filter; the intake valve body is connected to the intake duct through the valve body connector; the intake duct includes a plurality of intake holes, and along the width direction of the powertrain, the maximum distance between the two intake holes farthest apart is set to a first length, and the maximum length of the intake valve body along the width direction of the powertrain is set to a second length, and the ratio of the first length to the second length is greater than 0.66 and less than or equal to 0.96.

[0006] Further, the maximum length of the cylinder head along the width direction of the power assembly is set to a third length, and the ratio of the second length to the third length is greater than 0.68 and less than or equal to 0.99.

[0007] Furthermore, the air intake holes are arranged along the width direction of the powertrain, and the minimum distance between two adjacent air intake holes is set to be greater than or equal to 34 mm and less than or equal to 51 mm.

[0008] Furthermore, the valve body connector includes an air delivery hole arranged corresponding to the air inlet hole, and the valve body connector is fixedly connected to the cylinder head so that the air inlet hole is connected to the air delivery hole.

[0009] Furthermore, a connecting portion is provided on the cylinder head, and the connecting portion is provided around the air inlet hole. A fixing portion corresponding to the connecting portion is provided on the valve body connector, and the fixing portion is connected to the connecting portion, so that the valve body connector is connected to the cylinder head.

[0010] Further, along the length direction of the power assembly, the connecting parts at least partially overlap.

[0011] Furthermore, the valve body connector includes a rigid member for connecting the cylinder body and the intake valve body and an elastic member for buffering the cylinder body and the intake valve body, and the elastic member is arranged around the rigid member so that the rigid member and the elastic member are integrally formed.

[0012] Furthermore, the intake duct includes a first intake duct and a second intake duct. The first intake duct is located on one side of the cylinder head along the width direction of the power assembly, and the second intake duct is located on the other side of the cylinder head along the width direction of the power assembly. When observed along the height direction of the power assembly, the first intake duct and the second intake duct are basically arc-shaped.

[0013] Furthermore, the intake and exhaust mechanism includes an exhaust assembly, the maximum length of the exhaust assembly along the width direction of the powertrain is set to a fourth length, and the ratio of the first length to the fourth length is greater than 0.69 and less than or equal to 1.02.

[0014] Furthermore, the minimum distance between the intake valve body and the intake hole along the height direction of the powertrain is set to be greater than or equal to 28 mm and less than or equal to 42 mm.

[0015] The above-mentioned power assembly can adjust the spacing between the air intake ports to reduce the distance between the air intake ports, thereby making the structure between the air intake ports more compact, which is beneficial to improving the structural compactness of the cylinder head. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 It is a schematic diagram of the overall structure of the power assembly of the present invention.

[0017] Figure 2 It is an exploded view of the power assembly of the present invention.

[0018] Figure 3 It is a partial structural schematic diagram of the power assembly of the present invention.

[0019] Figure 4 It is a partial structural schematic diagram of the powertrain ignition device, cylinder head and cylinder block of the present invention.

[0020] Figure 5 It is a bottom view and a partial enlarged view of the cylinder head of the power assembly of the present invention.

[0021] Figure 6 It is an exploded view of the cylinder head and cylinder block of the power assembly of the present invention.

[0022] Figure 7 It is a rear view of the cylinder head of the power assembly of the present invention.

[0023] Figure 8It is a partial structural schematic diagram of the cylinder head and the intake and exhaust mechanism of the power assembly of the present invention. DETAILED DESCRIPTION

[0024] In order to enable those skilled in the art to better understand the solutions of the present invention, the technical solutions in the specific implementation modes of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the implementation modes of the present invention.

[0025] Figure 1 and Figure 2 A power assembly 100 is shown, which includes an outer shell 11, a crank-connecting rod mechanism 12, a piston mechanism 13, a valve mechanism 14, an ignition device 15, an intake and exhaust mechanism 16, and a speed change mechanism 17. An accommodation space 111 is formed in the outer shell 11, and the crank-connecting rod mechanism 12, the piston mechanism 13, the valve mechanism 14, the ignition device 15, the intake and exhaust mechanism 16, and the speed change mechanism 17 are all arranged in the accommodation space 111.

[0026] In this embodiment, the outer shell 11 includes a cylinder head cover 112, a cylinder head 113, a cylinder block 114, a crankcase 115 and an oil pan 116. The cylinder head cover 112, the cylinder head 113, the cylinder block 114, the crankcase 115 and the oil pan 116 are connected in sequence. Among them, a first accommodating space 1131 is formed in the cylinder head 113, and the ignition device 15, the valve mechanism 14 and the intake and exhaust mechanism 16 are at least partially arranged in the first accommodating space 1131. A second accommodating space 1141 is formed in the cylinder block 114, and the piston mechanism 13 is at least partially arranged in the second accommodating space 1141. Specifically, the cylinder block 114 is provided with a cylinder hole 1142 (refer to Figure 4 ), the piston mechanism 13 is at least partially disposed in the cylinder bore 1142. A third accommodating space 1151 is formed in the crankcase 115, and the crank-connecting rod mechanism 12 and the speed change mechanism 17 are at least partially disposed in the third accommodating space 1151.

[0027] As an implementation method, the combustion chamber of the power assembly 100 is composed of the bottom of the cylinder head 113 and the top of the cylinder body 114. The crank-connecting rod mechanism 12 is connected to the piston mechanism 13 so that the movement of the piston mechanism 13 can drive the crank-connecting rod mechanism 12 to move. The valve mechanism 14 is in transmission connection with the crank-connecting rod mechanism 12, and the valve mechanism 14 is in abutment with the intake and exhaust mechanism 16. The movement of the crank-connecting rod mechanism 12 can also drive the valve mechanism 14 to move, so that the valve mechanism 14 can control the intake and exhaust of the intake and exhaust mechanism 16. Through the above arrangement, the normal operation of the power assembly 100 can be achieved.

[0028] Specifically, the crank-connecting rod mechanism 12 includes a crankshaft 121 and a connecting rod 122, and the crankshaft 121 and the piston mechanism 13 are connected through the connecting rod 122 to achieve power transmission between the crankshaft 121 and the piston mechanism 13. The valve mechanism 14 includes a camshaft assembly 141 and a timing assembly 142, and the crankshaft 121 and the camshaft assembly 141 are transmission-connected through the timing assembly 142, so that the crankshaft 121 can drive the camshaft assembly 141 to move. The intake and exhaust mechanism 16 includes an intake component 161 and an exhaust component 162. The camshaft component 141 includes a camshaft 1411, a first cam 1412 and a second cam 1413. The first cam 1412 and the second cam 1413 are both arranged on the camshaft 1411. The first cam 1412 abuts against the intake component 161, and the second cam 1413 abuts against the exhaust component 162. The camshaft 1411 is connected to the crankshaft 121 through the timing component 142, so that the crankshaft 121 can drive the first cam 1412 on the camshaft 1411 to control the intake of the intake component 161, and the crankshaft 121 can drive the second cam 1413 on the camshaft 1411 to control the exhaust of the exhaust component 162. The speed change mechanism 17 includes a main shaft 171, a secondary shaft 172, a shift fork shaft 173 and a shift fork 174. The main shaft 171 is respectively connected to the crankshaft 121 and the secondary shaft 172. The main shaft 171 receives the power transmitted from the crankshaft 121 and transmits the power to the secondary shaft 172 through the meshing gear set, and then outputs the power to the outside through the secondary shaft 172. Specifically, a plurality of pairs of mutually cooperating shift gears are arranged on the main shaft 171 and the secondary shaft 172, and the power is transmitted through the shift gears. Among them, the shift fork 174 is at least partially sleeved on the shift fork shaft 173. A shift fork groove is arranged on the shift gear, and the shift fork 174 is at least partially located in the shift fork groove, so that the shift fork 174 can adjust the meshing relationship of the shift gear so that the speed change mechanism 17 transmits power with different multiples of transmission ratios. In order to clearly illustrate the technical solution of the present application, it is also defined as follows: Figure 1 In the present application, the length direction of the powertrain 100 refers to the front, rear, left, right, top, and bottom. Figure 1 The front-to-rear direction in the diagram, the width direction of the powertrain 100 refers to Figure 1 The left and right directions in the figure, the height direction of the powertrain 100 refers to Figure 1 The up and down directions in .

[0029] like Figure 3 and Figure 4As shown, as an implementation, an intake passage 1135 and an exhaust passage 1136 are formed in the cylinder head 113. The cylinder body 114 is connected to the cylinder head 113 and forms a combustion chamber 117. The intake passage 1135 is in communication with the combustion chamber 117 and includes an intake port 1135a. The exhaust passage 1136 is in communication with the combustion chamber 117 and includes an exhaust port 1136a. The ignition device 15 passes through the cylinder head 113 and is at least partially located in the combustion chamber 117. The intake and exhaust mechanism 16 includes an exhaust assembly 162, and the exhaust assembly 162 includes an exhaust pipe 1136b. The exhaust pipe 1136b is in communication with the exhaust passage 1136 to achieve exhaust of the power assembly 100.

[0030] As an implementation, the power assembly 100 further includes an air filter 22, which is in communication with the intake passage 1135, so that the air filter 22 can provide sufficient oxygen for the combustion chamber 117. The intake passage 1135 and the exhaust passage 1136 are both in communication with the cylinder bore 1142, and the intake passage 1135 extends substantially along the direction of the first preset straight line L1, defining a preset plane 104 perpendicular to the axis of the cylinder bore 1142, and the angle α between the first preset straight line L1 and the preset plane 104 is set to be greater than or equal to 30° and less than or equal to 62°. Specifically, the angle α between the first preset straight line L1 and the preset plane 104 is set to be greater than or equal to 38° and less than or equal to 54°. More specifically, the angle α between the first preset straight line L1 and the preset plane 104 is set to 46°. Through the above setting, it is possible to avoid the intake duct 1135 being too long in the height direction of the power assembly 100 due to the angle α between the first preset straight line L1 and the preset plane 104 being too large, so as to prevent the height of the cylinder head 113 from being too large, which is beneficial to improving the structural compactness of the cylinder head 113, and further to improving the space utilization of the power assembly 100; it is also possible to avoid the intake duct 1135 being too long in the length direction of the power assembly 100 due to the angle α between the first preset straight line L1 and the preset plane 104 being too small, so as to prevent the intake duct 1135 from being too tortuous, which is beneficial to reducing the intake resistance of the intake duct 1135, thereby improving the flow coefficient of the intake duct 1135, and further to improving the combustion efficiency of the power assembly 100.

[0031] As an implementation method, the air inlet 1135a is higher than the exhaust port 1136a along the height direction of the power assembly 100. Specifically, the gas in the outside flows into the combustion chamber 117 through the air inlet 1135a, and is mixed with the fuel in the combustion chamber 117 to form exhaust gas and then discharged through the exhaust port 1136a. At this time, the exhaust gas has a high heat, so the exhaust port 1136a is set at the lower end of the air inlet 1135a, so that the distance between the exhaust port 1136a and the ground is closer, so that the exhaust duct 1136 can be arranged close to the ground, so that the heat of the exhaust port 1136a can be conducted to the ground, so as to improve the heat dissipation of the cylinder head 113, and then help improve the heat dissipation efficiency of the power assembly 100.

[0032] In this embodiment, the length L2 of the air inlet 1135 along the first preset straight line L1 is set to be greater than or equal to 96 mm and less than or equal to 141 mm. Specifically, the length L2 of the air inlet 1135 along the first preset straight line L1 is set to be greater than or equal to 106 mm and less than or equal to 128 mm. More specifically, the length L2 of the air inlet 1135 along the first preset straight line L1 is set to be greater than 116 mm. Through the above-mentioned arrangement, it is possible to avoid the intake volume of the intake duct 1135 being too low due to the length L2 of the intake duct 1135 along the first preset straight line L1 being too large, so as to prevent the flow coefficient of the intake duct 1135 from being too low, which is beneficial to improving the tumble ratio of the intake duct 1135, and further beneficial to improving the combustion efficiency of the combustion chamber 117; it is also possible to avoid the height of the cylinder block 114 being too low due to the length L2 of the intake duct 1135 along the first preset straight line L1 being too small, so as to prevent the connection between the cylinder block 114 and the air filter 22 from being unstable, which is beneficial to improving the connection stability between the cylinder block 114 and the air filter 22, and further improving the structural stability of the powertrain 100.

[0033] As an implementation, the exhaust passage 1136 extends substantially along the exhaust direction 105, and the length L3 of the exhaust passage 1136 along the exhaust direction 105 is set to be greater than or equal to 44 mm and less than or equal to 65 mm. Specifically, the length L3 of the exhaust passage 1136 along the exhaust direction 105 is set to be greater than or equal to 49 mm and less than or equal to 59 mm. More specifically, the length L3 of the exhaust passage 1136 along the exhaust direction 105 is set to be greater than or equal to 54 mm. The exhaust direction 105 refers to the flow direction of the exhaust gas in the exhaust passage 1136. Through the above-mentioned arrangement, it is possible to avoid a reduction in the exhaust gas fluidity in the combustion chamber 117 due to the length L3 of the exhaust duct 1136 along the exhaust direction 105 being too large, thereby preventing the combustion efficiency of the combustion chamber 117 from being reduced, which is beneficial to improving the combustion efficiency of the combustion chamber 117; it is also possible to avoid an unstable connection between the exhaust duct 1136 and the exhaust pipe 1136b due to the length L3 of the exhaust duct 1136 along the exhaust direction 105 being too small, which is beneficial to improving the connection stability between the exhaust duct 1136 and the exhaust pipe 1136b.

[0034] As an implementation, the ratio of the maximum cross-sectional area of ​​the air inlet 1135a along the first preset straight line L1 to the maximum cross-sectional area of ​​the exhaust port 1136a along the exhaust direction 105 is greater than or equal to 1.06 and less than or equal to 1.55. Further, the ratio of the maximum cross-sectional area of ​​the air inlet 1135a along the first preset straight line L1 to the maximum cross-sectional area of ​​the exhaust port 1136a along the exhaust direction 105 is greater than or equal to 1.16 and less than or equal to 1.41. Further, the ratio of the maximum cross-sectional area of ​​the air inlet 1135a along the first preset straight line L1 to the maximum cross-sectional area of ​​the exhaust port 1136a along the exhaust direction 105 is 1.28. Through the above-mentioned arrangement, it is possible to avoid the air intake port 1135a occupying a larger space due to the ratio of the maximum cross-sectional area of ​​the air intake port 1135a along the first preset straight line L1 to the maximum cross-sectional area of ​​the exhaust port 1136a along the exhaust direction 105 being too large, so as to prevent the exhaust speed of the exhaust duct 1136 from being reduced, which is beneficial to improving the exhaust efficiency of the exhaust duct 1136, and further to improving the combustion efficiency of the combustion chamber 117; it is also possible to avoid the exhaust port 1136a occupying a larger space due to the ratio of the maximum cross-sectional area of ​​the air intake port 1135a along the first preset straight line L1 to the maximum cross-sectional area of ​​the exhaust port 1136a along the exhaust direction 105 being too small, so as to prevent the intake speed of the air intake duct 1135 from being slowed down, which is beneficial to improving the intake efficiency of the air intake duct 1135, and further to improving the combustion efficiency of the combustion chamber 117.

[0035] As an implementation, the ignition device 15 extends substantially along the direction of the second preset straight line L4, the second preset straight line L4 is substantially perpendicular to the preset plane 104, the air inlet 1135a and the exhaust port 1136a are arranged around the second preset straight line L4, so that the air inlet 1135 and the exhaust 1136 are arranged around the ignition device 15. Through the above arrangement, the structures of the air inlet 1135, the exhaust 1136 and the ignition device 15 can be made more compact, which is conducive to improving the structural compactness of the air inlet 1135, the exhaust 1136 and the ignition device 15, and further conducive to improving the structural compactness of the power assembly 100.

[0036] As an implementation method, a projection plane 101 perpendicular to the width direction of the powertrain 100 is defined, a first preset straight line L1 is projected in the projection plane 101 along the width direction of the powertrain 100 as a first projection line, a second preset straight line L4 is projected in the projection plane 101 along the width direction of the powertrain 100 as a second projection line, and an angle β between the first projection line and the second projection line is set to be greater than or equal to 28° and less than or equal to 60°. Specifically, the angle β between the first projection line and the second projection line is set to be greater than or equal to 36° and less than or equal to 52°. More specifically, the angle β between the first projection line and the second projection line is set to be greater than or equal to 44°. Through the above-mentioned arrangement, it is possible to avoid the curvature of the air intake duct 1135 close to the ignition device 15 becoming larger due to the angle β between the first projection line and the second projection line being too large, so as to prevent the intake resistance of the air intake duct 1135 from increasing, which is beneficial to improving the flow coefficient of the air intake duct 1135; it is also possible to avoid the air intake duct 1135 being set close to the ignition device 15 due to the angle β between the first projection line and the second projection line being too small, so as to prevent the air intake duct 1135 from interfering with the ignition device 15, which is beneficial to improving the rationality of the layout of the air intake duct 1135 and the ignition device 15.

[0037] As an implementation, the cylinder block 114 includes a cylinder block combustion chamber 1144, the cylinder head 113 includes a cylinder head combustion chamber 1137, the cylinder block combustion chamber 1144 and the cylinder head combustion chamber 1137 are machined, and the cylinder block combustion chamber 1144 and the cylinder head combustion chamber 1137 are connected to form the combustion chamber 117. Specifically, the precision of the cylinder block combustion chamber 1144 and the cylinder head combustion chamber 1137 can be made higher through machining, so as to improve the sealing performance of the combustion chamber 117, thereby facilitating the improvement of the sealing performance of the power assembly 100.

[0038] like Figure 5As shown, in this embodiment, two air inlets 1135a are provided in the cylinder head combustion chamber 1137, and the minimum distance D1 between the two air inlets 1135a of the air inlet hole 1135b is set to be greater than 1.9 mm and less than or equal to 2.8 mm. Specifically, the minimum distance D1 between the two air inlets 1135a of the air inlet hole 1135b is set to be greater than 2.1 mm and less than or equal to 2.5 mm. More specifically, the minimum distance D1 between the two air inlets 1135a of the air inlet hole 1135b is set to be greater than 2.3 mm. Through the above-mentioned arrangement, it is possible to avoid the space of the cylinder head combustion chamber 1137 being too large due to the minimum distance D1 between the two air inlets 1135a of the air inlet hole 1135b being too large, so as to avoid the cylinder head combustion chamber 1137 occupying a larger space, thereby helping to improve the space utilization of the cylinder head 113; it is also possible to avoid the wall thickness between the air inlet holes 1135b being too thin due to the minimum distance D1 between the two air inlet ports 1135a of the air inlet hole 1135b being too small, so as to prevent the structural strength of the intake duct 1135 from being reduced, thereby helping to improve the structural strength of the intake duct 1135.

[0039] As an implementation, two exhaust ports 1136a are provided in the cylinder head combustion chamber 1137, and the minimum distance D2 between the two exhaust ports 1136a is set to be greater than 3.9 mm and less than or equal to 5.7 mm. Specifically, the minimum distance D2 between the two exhaust ports 1136a is set to be greater than 4.3 mm and less than or equal to 5.2 mm. More specifically, the minimum distance D2 between the two exhaust ports 1136a is set to be greater than 4.7 mm. Through the above-mentioned setting, it is possible to avoid the cylinder head combustion chamber 1137 from being too large due to the minimum distance D2 between the two exhaust ports 1136a being too large, so as to avoid the cylinder head combustion chamber 1137 from occupying a large space, thereby facilitating the improvement of the space utilization rate of the cylinder head 113; it is also possible to avoid the wall thickness between the exhaust ports 1136a being too thin due to the minimum distance D2 between the two exhaust ports 1136a being too small, so as to prevent the structural strength of the exhaust passage 1136 from being reduced, thereby facilitating the improvement of the structural strength of the exhaust passage 1136.

[0040] like Figure 6As shown, as an implementation, the intake and exhaust mechanism 16 includes a plurality of valve body connectors 164 and an intake valve body 163, the intake valve body 163 is in communication with the air filter 22, and the intake valve body 163 is connected to the intake passage 1135 through the valve body connector 164. Specifically, the air filter 22 is in communication with the outside world, and transmits the outside gas to the intake passage 1135 through the intake valve body 163 and the valve body connector 164, and the intake passage 1135 is in communication with the combustion chamber 117, so that the combustible gas formed by the outside gas and the fuel enters the combustion chamber 117. Through the above arrangement, the structure of the intake valve body 163, the valve body connector 164 and the intake passage 1135 is more compact, which is conducive to improving the structural compactness of the intake valve body 163, the valve body connector 164 and the intake passage 1135, and further conducive to improving the flow coefficient of the intake passage 1135.

[0041] As an implementation, the air intake passage 1135 includes an air intake hole 1135b, and along the width direction of the power assembly 100, the maximum distance between the two air intake holes 1135b that are farthest apart is set to a first length L5, and the maximum length of the air intake valve body 163 along the width direction of the power assembly 100 is set to a second length L6, and the ratio of the first length L5 to the second length L6 is greater than 0.66 and less than or equal to 0.96. Specifically, the ratio of the first length L5 to the second length L6 is greater than 0.72 and less than or equal to 0.88. More specifically, the ratio of the first length L5 to the second length L6 is greater than 0.8. Through the above-mentioned arrangement, it is possible to avoid the volume of the intake valve body 163 being too large due to the ratio of the first length L5 to the second length L6 being too large, so as to prevent the intake valve body 163 from occupying a larger space, thereby helping to improve the space utilization of the power assembly 100; it is also possible to avoid the distance between the intake holes 1135b being too close due to the ratio of the first length L5 to the second length L6 being too small, so as to prevent interference between the intake holes 1135b, thereby helping to improve the rationality of the layout between the intake holes 1135b, and the compact structure between the intake ports 1135a, which is further helpful to improve the structural compactness of the cylinder block 114.

[0042] As an implementation, the maximum length of the cylinder head 113 along the width direction of the power assembly 100 is set to the third length L7, and the ratio of the second length L6 to the third length L7 is greater than 0.68 and less than or equal to 0.99. Specifically, the ratio of the first second length L6 to the third length L7 is greater than 0.75 and less than or equal to 0.90. More specifically, the ratio of the second length L6 to the third length L7 is 0.82. Through the above setting, it is possible to avoid the excessive width of the intake valve body 163 due to the excessively large ratio of the second length L6 to the third length L7, so as to prevent the intake valve body 163 from occupying a large space, thereby facilitating the improvement of the space utilization of the power assembly 100; it is also possible to avoid the excessive volume of the intake valve body 163 due to the excessively small ratio of the second length L6 to the third length L7, so as to prevent the intake valve body 163 from occupying a large space, thereby facilitating the improvement of the structural compactness of the power assembly 100.

[0043] like Figure 7 As shown, as an implementation, the air inlet holes 1135b are arranged along the width direction of the powertrain 100, and the minimum distance D3 between two adjacent air inlet holes 1135b is set to be greater than or equal to 34mm and less than or equal to 51mm. Specifically, the minimum distance D3 between two adjacent air inlet holes 1135b is set to be greater than or equal to 38mm and less than or equal to 46mm. More specifically, the minimum distance D3 between two adjacent air inlet holes 1135b is set to be greater than or equal to 42mm. Through the above-mentioned arrangement, it is possible to avoid the width of the cylinder head 113 being too wide due to the minimum distance D3 between two adjacent intake holes 1135b being too large, thereby preventing the cylinder head 113 from occupying a larger space, thereby facilitating improving the structural compactness between the intake holes 1135b; it is also possible to avoid the wall thickness between the intake holes 1135b being too thin due to the minimum distance D3 between two adjacent intake holes 1135b being too small, thereby preventing the strength of the intake duct 1135 from being reduced, thereby facilitating improving the structural compactness of the intake duct 1135.

[0044] like Figure 7 and Figure 8As shown, as an implementation, the valve body connector 164 includes a gas delivery hole 1641 corresponding to the air inlet hole 1135b, and the valve body connector 164 is fixedly connected to the cylinder head 113, so that the air inlet hole 1135b is connected with the gas delivery hole 1641. Specifically, the axis of the air delivery hole 1641 and the air inlet hole 1135b are substantially coincident, and the sizes of the air inlet hole 1135b and the air delivery hole 1641 are substantially consistent, so that the external gas passes through the gas delivery hole 1641 and the air inlet hole 1135b into the combustion chamber 117. Through the above arrangement, the intake resistance of the external gas during the intake process can be reduced, which is conducive to improving the flow coefficient between the valve body connector 164 and the air inlet hole 1135b, and further conducive to improving the combustion efficiency of the combustion chamber 117.

[0045] As an implementation method, the cylinder head 113 is provided with a plurality of connecting parts 1138, the connecting parts 1138 are arranged around the air inlet hole 1135b, and the valve body connector 164 is provided with a fixing part 1642 corresponding to the connecting part 1138, the fixing part 1642 is arranged around the air delivery hole 1641, and the fixing part 1642 is connected to the connecting part 1138, so that the valve body connector 164 is connected to the cylinder head 113. Specifically, at least two connecting parts 1138 are arranged corresponding to each exhaust hole, so that the connection between the valve body connector 164 and the cylinder head 113 is more stable, and at the same time, the connecting surface of the valve body connector 164 and the cylinder head 113 is closely fitted, which is also conducive to improving the sealing performance of the air delivery hole 1641 and the air inlet hole 1135b.

[0046] As an implementation, along the length direction of the power assembly 100, the connection parts 1138 at least partially overlap. Specifically, at least two connection parts 1138 are arranged between the air inlet holes 1135b, each connection part 1138 is respectively connected to one air inlet hole 1135b, and the two connection parts 1138 are basically staggered, that is, one of the connection parts 1138 is at least partially arranged on the front side or the rear side of the other connection part 1138, so that the connection parts 1138 at least partially overlap in the length direction of the power assembly 100, and the structure between the air inlet holes 1135b is made more compact without affecting the connection stability between the valve body connector 164 and the cylinder head 113. Through the above arrangement, the structural compactness between the air inlet holes 1135b can be improved, thereby improving the structural compactness of the valve body connector 164 and the cylinder head 113, and further improving the space utilization of the power assembly 100.

[0047] As an implementation method, the valve body connector 164 includes a rigid part (not shown) for connecting the cylinder body 114 and the intake valve body 163 and an elastic part (not shown) for buffering the cylinder body 114 and the intake valve body 163. The elastic part is arranged around the rigid part so that the rigid part and the elastic part are integrally formed. Specifically, the elastic part can be set to a material such as rubber so that the elastic part has both buffering and sealing properties, and the rigid part can be set to a material such as metal so that the rigid part has a certain strength and toughness. Through the above arrangement, through the mutual cooperation between the elastic part and the rigid part, the connection strength between the valve body connector 164 and the cylinder body 114 can be improved, and at the same time, the sealing performance of the valve body connector 164 and the cylinder body 114 can be improved.

[0048] like Figure 8 As shown, as an implementation, the air intake passage 1135 includes a first air intake passage 1135c and a second air intake passage 1135d, the first air intake passage 1135c is located on one side of the cylinder head 113 along the width direction of the power assembly 100, and the second air intake passage 1135d is located on the other side of the cylinder head 113 along the width direction of the power assembly 100, and the first air intake passage 1135c and the second air intake passage 1135d are both substantially arc-shaped when viewed along the height direction of the power assembly 100. Specifically, since the maximum width of the first air intake passage 1135c and the second air intake passage 1135d is greater than the first length L5, the air intake passage 1135 in the cylinder head 113 can be arranged in an arc shape to avoid interference between the air intake passages 1135, and the flow coefficient of the air intake passage 1135 remains unchanged. Through the above arrangement, the structure between the air intake passages 1135 is more compact, which is conducive to improving the compactness of the structure between the air intake passages 1135.

[0049] like Figure 6 and Figure 8As shown, as an implementation, the intake and exhaust mechanism 16 includes an exhaust assembly 162, and the exhaust assembly 162 is used to exhaust the exhaust gas in the cylinder body 114. Among them, the maximum length of the exhaust assembly 162 along the width direction of the power assembly 100 is set to the fourth length L8, and the ratio of the first length L5 to the fourth length L8 is greater than 0.69 and less than or equal to 1.02. Specifically, the ratio of the first length L5 to the fourth length L8 is greater than 0.76 and less than or equal to 0.93. More specifically, the ratio of the first length L5 to the fourth length L8 is 0.85. Through the above-mentioned arrangement, it is possible to avoid the width of the exhaust component 162 being too small due to the ratio of the first length L5 to the fourth length L8 being too large, so as to prevent the exhaust efficiency of the exhaust component 162 from being reduced and the exhaust gas in the cylinder body 114 from being unable to be completely discharged, which is beneficial to improving the flow coefficient of the cylinder body 114 and the exhaust component 162, and further beneficial to improving the exhaust efficiency of the cylinder body 114 and the exhaust component 162; it is also possible to avoid the volume of the exhaust component 162 being too large due to the ratio of the first length L5 to the fourth length L8 being too small, so as to prevent the exhaust component 162 from occupying a larger space, and further beneficial to improving the space utilization of the powertrain 100.

[0050] As an implementation, the minimum distance D4 between the intake valve body 163 and the intake hole 1135b along the height direction of the power assembly 100 is set to be greater than or equal to 28 mm and less than or equal to 42 mm. Specifically, the minimum distance D4 between the intake valve body 163 and the intake hole 1135b along the height direction of the power assembly 100 is set to be greater than or equal to 32 mm and less than or equal to 38 mm. More specifically, the minimum distance D4 between the intake valve body 163 and the intake hole 1135b along the height direction of the power assembly 100 is set to be greater than or equal to 35 mm. Through the above arrangement, it is possible to avoid the intake valve body 163 being set too high along the height direction of the power assembly 100 due to the minimum distance D4 between the intake valve body 163 and the intake hole 1135b being too large, so as to prevent the intake valve body 163 from occupying a large space, thereby facilitating the improvement of the space utilization rate of the power assembly 100; it is also possible to avoid the valve body connector 164 being too small due to the minimum distance D4 between the intake valve body 163 and the intake hole 1135b along the height direction of the power assembly 100 being too small, thereby preventing the stability of the valve body connector 164 and the cylinder body 114 from being reduced. This is further conducive to improving the structural stability of the power assembly 100.

[0051] It should be understood that those skilled in the art can make improvements or changes based on the above description, and all these improvements and changes should fall within the scope of protection of the appended claims of the present invention.

Claims

1. A powertrain, comprising: a cylinder head, wherein a plurality of intake passages are formed in the cylinder head; a cylinder body, the cylinder body being connected to the cylinder head and forming a combustion chamber, the intake passage being in communication with the combustion chamber; an air filter, the air filter being in communication with the air intake duct; The intake and exhaust mechanism comprises an intake valve body and a valve body connector, the intake valve body is communicated with the air filter, and the intake valve body is connected to the intake passage through the valve body connector; characterized in that: The intake duct includes a plurality of intake holes. Along the width direction of the power assembly, the maximum distance between the two intake holes that are farthest apart is set to a first length. The maximum length of the intake valve body along the width direction of the power assembly is set to a second length. The ratio of the first length to the second length is greater than 0.66 and less than or equal to 0.

96.

2. The powertrain according to claim 1, characterized in that: The maximum length of the cylinder head along the width direction of the power assembly is set to a third length, and a ratio of the second length to the third length is greater than 0.68 and less than or equal to 0.

99.

3. The powertrain according to claim 1, characterized in that: The air intake holes are arranged along the width direction of the power assembly, and the minimum distance between two adjacent air intake holes is set to be greater than or equal to 34 mm and less than or equal to 51 mm.

4. The powertrain according to claim 1, characterized in that: The valve body connector includes an air delivery hole corresponding to the air inlet hole, and the valve body connector is fixedly connected to the cylinder head so that the air inlet hole is connected to the air delivery hole.

5. The powertrain according to claim 4, characterized in that: The cylinder head is provided with a connecting portion, which is arranged around the air inlet hole. The valve body connector is provided with a fixing portion corresponding to the connecting portion, which is connected to the connecting portion, so that the valve body connector is connected to the cylinder head.

6. The powertrain according to claim 1, characterized in that: Along the length direction of the power assembly, the connecting parts at least partially overlap.

7. The powertrain according to claim 1, characterized in that: The valve body connector includes a rigid member for connecting the cylinder body and the intake valve body and an elastic member for buffering the cylinder body and the intake valve body. The elastic member is arranged around the rigid member so that the rigid member and the elastic member are integrally formed.

8. The powertrain according to claim 1, characterized in that: The intake duct includes a first intake duct and a second intake duct. The first intake duct is located on one side of the cylinder head along the width direction of the power assembly, and the second intake duct is located on the other side of the cylinder head along the width direction of the power assembly. When observed along the height direction of the power assembly, the first intake duct and the second intake duct are basically arc-shaped.

9. The powertrain according to claim 1, characterized in that: The intake and exhaust mechanism includes an exhaust component, the maximum length of the exhaust component along the width direction of the powertrain is set to a fourth length, and the ratio of the first length to the fourth length is greater than 0.69 and less than or equal to 1.

02.

10. The powertrain according to claim 1, characterized in that: The minimum distance between the intake valve body and the intake hole along the height direction of the power assembly is set to be greater than or equal to 28 mm and less than or equal to 42 mm.

Images