JPS60138265A - Intake device for v-type multi-cylinder internal- combustion engine - Google Patents

Abstract

PURPOSE:To make variable the effective length of intake tube easily by arranging an intake manifold between cylinder rows at the right and left of V-type multi-cylinder internal-combustion engine while constructing it with high and low intake paths. CONSTITUTION:An intake manifold M is arranged through a groove V between the left and right cylinder rows C, C of V-type 6-cylinder engine for the purpose to distribute the intake-air to three intake ports 141-143 in the left and right cylinder rows C. Said manifold M is comprised of common intake distribution chamber 16, high speed intake paths 171-173 extending from one side of said chamber 16 to each intake port 141-143 and low speed intake paths 181-183 extending from the other side of said chamber 16 to be coupled to the sections b1-b3 branched from the intermediate section of intake path 171-173. Valves 241-243 for opening/closing each high speed intake path 171-173 are provided on an intermediate board P placed at the intermediate section of said manifold M to vary the effective length of intake tube through opening/closing of said valves 241-243.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an intake system for a V-type multi-cylinder internal combustion engine, in which a pair of cylinder rows each having a plurality of cylinders arranged in the axial direction of a crankshaft are arranged in a V-shape. The purpose of this is to automatically change the effective pipe length of the intake system depending on the engine's low-speed and high-speed operating conditions, and to effectively utilize the intake inertia effect during both low-speed and high-speed operation. In order to sufficiently increase charging efficiency and always provide stable high-output performance to the engine, the multiple high-speed and low-speed intake passages necessary for this purpose are arranged by effectively utilizing the valleys between both cylinder rows. Therefore, it is an object of the present invention to provide an effective and compact air intake device that does not significantly increase the overall height of the engine.

To achieve this objective, the present invention provides a plurality of intake ports that are connected to a plurality of intake ports of each cylinder row, converge in the valley of both cylinder rows, and extend linearly outward from the valley along the axis of the crankshaft. A plurality of independent high-speed intake passages, an intake distribution chamber arranged in parallel in the valley to open the entrance of each high-speed intake passage, and a branch opening provided in the middle of each high-speed intake passage; An intake manifold is constituted by a plurality of low-speed intake passages whose inlets open into the intake distribution chamber, and the length of each high-speed intake passage is determined by the length of each of the high-speed intake passages, which corresponds to the length of each of the low-speed intake passages and each of the passages downstream of the branch port. Each of the high-speed intake passages upstream of the branch port is provided with an on-off valve that opens and closes the high-speed intake passage, the length being shorter than the total length of the high-speed intake passage. A feature is that an actuator is connected to open the on-off valve.

An embodiment of the present invention will be described below with reference to the drawings.

5- The internal combustion engine shown in Figure 1 is a V-type six-cylinder engine, and therefore has two cylinder rows C arranged in a V-shape on the left and right sides.
2C' is provided with three cylinders 1 arranged in the axial direction (front and back direction in FIG. 1) of a crankshaft (not shown).

Since the structures of both cylinder rows C and CI are approximately symmetrical, only the structure of the left cylinder row C will be explained.A cylinder head 3 is superimposed on the upper surface of a cylinder block 2 in which cylinders 1 are formed via a gasket 4. and is bound. A piston 5 is slidably fitted into the cylinder 1, and a combustion chamber 6 is recessed in the bottom surface of the cylinder head 3 facing the piston 5.

The ceiling surface 7 of the combustion chamber 6 has two slopes 7α that descend from a ridge line extending in the direction in which the three cylinders 1 are arranged toward both the left and right sides.
, 7h (see Fig. 1A), a pair of intake valve ports 8, 8 are located on the slope 7a located on the valley V side between both cylinder rows C and C1, and a slope 6- on the opposite side. Similarly, in 7b K, a pair of exhaust valve ports 9, 9 are opened side by side along the ridgeline, and these intake valve ports 8, 8 and exhaust valve ports 9, 9 are each a pair driven by a valve mechanism 10. are opened and closed by intake valves ii, 1i and exhaust valves 12.12, respectively. These four valves 11, 11;
One ignition plug 13 surrounded by 12, 12 is screwed onto the cylinder head 3, and its electrode faces the center of the ceiling surface 7 of the combustion chamber 6.

Each pair of intake valve ports 8, 8 and exhaust valve ports 9, 9 are connected to a common intake boat 14 and exhaust port 15, respectively,
The inlet of the intake port 140 opens on the upper surface of one side of the cylinder head 3 adjacent to the valley V, and the outlet of the exhaust port 15 opens on the other side of the cylinder head 3.

In FIG. 2, the three intake ports of the left cylinder row C are arranged in order from the top. Second. 3rd intake port) 14+, 1
42-143, and the three intake boats of the right cylinder row C' are numbered 1], 2. Third intake port 14. ', 142'.

Let's call it 143'. Intake manifold M for distributing and supplying air or mixture to these intake boats
is arranged through the valley V.

As shown in FIGS. 2 to 7, this intake manifold M includes one common intake distribution chamber 16 and this distribution chamber 16.
Extending from one side of the left side, the first to third intake ports 14. ~
143 respectively on the left side first to third high-speed intake passages 17.
173, and the first to third left air intake passages 17. which extend from the other side of the air intake distribution chamber 16. The branch openings provided at the intermediate portions of ~1γ3, the left side first to third low-speed intake passages 181 to 183, respectively connected to ~b3, and the right side first to right side low-speed intake passages extending from one side of the intake distribution chamber 16, respectively connect to ~b3. 3 intake boat 14. '~143'
Right side first to third high-speed intake passages 17. '~1
73' and a first right side extending from the other side of the intake distribution chamber 16.
~Third intake path 17. - 173' are connected to the branch ports 61' to b3' provided at the intermediate portions of the right side first to third low-speed intake passages 18. ' to 183'.

In addition, the intake manifold M has a first block B disposed in the valley V in order to facilitate its processing, assembly, maintenance, etc.
1, the third intake port in the valley r) 143°143', the second block B2 disposed on the outer side, and both blocks B.
The intermediate plate P is interposed between B2 and is divided into three parts. 1st
A pair of horizontal mounting flanges 19, 19' are integrally formed on the block B1, corresponding to the left and right cylinder rows C, C'. It is fixed to the cylinder heads 3 and 3' through a plurality of poles (20° and 20'), respectively. Also, the first and second blocks 13. , B2 are also integrally formed with connecting flanges 21.9-22 at opposite ends thereof, and both connecting flanges 21.22 are connected to each other by a plurality of bolts 23 with the intermediate plate P in between. Ru.

The intake air distribution chamber 16 is formed in the second block B so as to have a basic shape of a cylinder longer than the maximum width of the valley V and to face in a horizontal direction perpendicular to a crankshaft (not shown). and the first intake port farthest from the intake distribution chamber 16) 140.14
The first high-speed intake passages 17t-17t' connected to the first high-speed intake passages 17t-17t' are arranged left and right in the center of the valley V, pass through the first block B1, penetrate the intermediate plate P, and open into the chamber 16. 18
1°181' is the corresponding first block in the first block B.
Passing under the high-speed intake passages 17+ and 171', the intermediate plate P
After penetrating through the distribution chamber 16, it is turned upward from the lower side of the distribution chamber 16 and opens at the upper surface of the chamber 16. Also, the second high-speed intake passage 172.
172' are arranged left and right in the center of the valley V to form the first high-speed intake 10-path 17. in the first block B. ,17. The second low-speed intake passage 18□ passes through a part of the ', passes through the intermediate plate P, and opens into the distribution chamber 16.

18□' passes above the corresponding second high-speed intake passages 17□ and 17□' in the first block B, passes through the intermediate plate P, and then turns downward from the upper side of the distribution chamber 16 to fill the chamber 1.
Opens on the bottom surface of 6. Furthermore, the third high-speed intake passage 171,1
7. ' passes through the first block B adjacent to the left and right sides of the second intake passage 172', 17□l, penetrates the intermediate plate P and opens into the distribution chamber 16, and the third low-speed intake passage 183.183'
is the corresponding third high-speed intake passage 1 in the first block B1.
7. ．． After passing through the upper side of 173' and penetrating the intermediate plate P,
The dispensing chamber 11 is turned downward from upstream to open into the chamber 16 .

First to third high-speed intake passages 17. ~i7. ．． ;17. '~1
73' are the first to third low-speed intake passages 18., each having a corresponding cross-sectional area. ~183;18. It is formed to be more dog-like than that of '~183'. In addition, these high-speed intake passages 1
7. ~173;17. '~17. ′ extend linearly along the axis of the crankshaft, and the inlet ends a1 to a3; a, ′ to
The length of entry of a and ' into the intake air distribution chamber 16 is adjusted. That is, 1st. Second. Third high-speed intake passage 17. ~173;17
．． '~17. 'In the order of inlet end a, ~a3jal'~a3
' is increased, and in the illustrated example, the first high-speed intake passage 17. ．． 17. It is assumed that the plunge length of the entrance ends a, , a, and ' is zero.

Furthermore, each low-speed intake passage 18. ~183;18. '～183
' Length of branch port ~b3; b, '~A3/ Each high-speed intake path 171-173 on the downstream side; 17. '~17
3' is approximately equal to the first length, and the sum of the lengths of each high-speed intake passage 17. ~173;17. The second length is set to be larger than the second length, which is ~173'. Therefore, the first length is a length that can maximize the charging efficiency due to the intake inertia effect when the engine is running at low speed, and the second length is the length that can maximize the charging efficiency due to the intake inertia effect when the engine is running at high speed. It is a length that can be increased to

As shown in FIG. 1, with the above configuration, high and low speed intake passages are arranged on the intermediate plate P as follows.

That is, the left third low-speed intake passage 183 is located at the top stage in order from the left.
, the second low-speed intake passage 182, and the second low-speed intake passage 182 on the right side.
', the third low-speed intake passage 1831, and the second stage, from left to right, the third high-speed intake passage 173 on the left, and the second high-speed intake passage 17□
, right second high-speed intake passage 1γ2/.

The third high-speed intake passage 173', the third stage is the left first high-speed intake passage 177, the right-hand first high-speed intake passage 171', the bottom stage is the left first low-speed intake passage 181, the right first low-speed Intake path 18. ′.

The intermediate plate P has first to third high-speed intake passages 171 to 173, respectively.
; Butterfly type on-off valve 24 that opens and closes 171' to 173'. ~243;24. '~243' are pivotally supported.

The four on-off valves 243, 242;
; 172', 173' are horizontally traversed by the long first valve shaft 25□ supported by the intermediate plate P;
on-off valves 24+, 24. ' is the high-speed intake path 17,
．． 17. ' is carried by a short second valve shaft 252 which is supported by the intermediate plate P horizontally across the valve. As shown in FIG. 3, both valve shafts 25. , 252 each have an operating lever 2 at the outer end.
6. ．． 262, these operating levers 26. ．．
262 are interconnected via interlock links 27 and to an actuator 28 responsive to a predetermined high speed condition of the engine. With this configuration, it is possible to centrally arrange a plurality of on-off valves without interfering with any of the intake passages, simplifying the on-off mechanism, and it is possible to form an assembly of the intermediate plate and the on-off valves. The overall assemblability is improved.

As the actuator 28, a type 14 type such as a negative pressure type or an electromagnetic type can be adopted, but in the case of a negative pressure type, the opening/closing valve is closed by the boost negative pressure of the engine and opened by the force of a spring. It is desirable to configure it so that

Total 6 low speed intake passages 18. ~18. ;18. '~18,
' are arranged along the axial direction around the cylindrical intake distribution chamber 16 and are connected to each other so as to share a boundary wall, and the arrangement order is as follows: 183, the second low speed intake path 182, the first low speed intake path 181, the first right low speed intake path 181', the second low speed intake path 182', and the third low speed intake path 183'. There is. That is, the intake port 1 closest to the intake distribution chamber 16
Left and right third low-speed intake passages 18S are connected to 43 and 143', respectively.

183' are arranged at both ends of the intake air distribution chamber 160.

As shown in FIG. 7, the intake air distribution chamber 16 has a corrugated inner circumferential wall 29 surrounding it (the six low-speed air intake passages connected to each other).
and 5. A closed end wall 30 connected to one end of the inner peripheral wall 29
defined by. Therefore, in this case, there is no need to provide a special box for forming the intake air distribution chamber 16, and the structure is simple.

The other end of the air intake distribution chamber 16 is open as its inlet 16a, and a mounting surface 31 is formed around it.

A mounting flange 33 of a throttle valve cylinder 32 is fixed to this mounting surface 31 with bolts 34. The throttle valve cylinder 32 also has a distribution chamber 1.
6 primary and secondary intake passages 35□.

352, a primary throttle valve 361 is provided in the primary intake path 351, and a secondary throttle valve 362 is provided in the secondary intake path 352.
are provided respectively. An air cleaner 37 is attached to the inlet of the throttle valve cylinder 32.

As shown in FIGS. 1 and 2, each intake port 14. ~143;14t'~14. ' Fuel injection nozzle 38° to 383 ; 38
．． '~383' are installed.

Next, the operation of this embodiment will be explained. When the engine is operating at low speed, the actuator 28 is in an inactive state, and the on-off valves 241 to 241 are in an inactive state.
243; Close 241' to 243' and open high-speed intake path 1
71 to 1r3;1y,' to 1731 are all blocked. Therefore, the primary intake passage 35 is purified by the air cleaner 37 during the intake stroke of the engine. (and the secondary intake passage 352), the air is sucked into the primary throttle valve 36. (and the secondary throttle valve 362), the air flows into the intake distribution chamber 16, and from the classroom 16 there are six low-speed intake passages 181.
~183; 18, distributed to l~1831, branching port b
1~h3; 1,, l, l, 3/ to high speed intake path 171
~173;1γ,'~17. ', and the intake port 14° to 14. ; Sucked into the corresponding cylinder 1 via 141' to 143'. During this time, the fuel injection nozzles 38, to 383;38. '~383' Fuel enters the intake port 17-port 14. ~143: 14+'~143' are injected, and they are supplied into each cylinder 1 together with the above air.

Therefore, as mentioned above, the total length of each low-speed intake passage and the high-speed intake passage downstream from its branch port is compared in such a way that the charging efficiency can be maximized due to the intake inertia effect during low-speed operation of the engine. Since the first length is set to the target long first length, it is possible to satisfy the low speed output performance of the engine.
Since the intake manifold M is arranged in the longitudinal direction and surrounds the intake manifold 16, the intake manifold M as a whole is relatively compact, and both cylinder rows C2C
The amount of overhang from the valley V between 1 and 1 can be small.

When the engine enters a predetermined high-speed operating state, the actuator 28 is actuated to close the on-off valve 24. ~24. ; 241' to 243' are opened, and the high speed intake path 17. ~173;17. '~18-17,' are all electrically connected. Then, during the intake stroke of the engine, the air in the intake air distribution chamber 16 flows through the low-speed intake passages 181 to 183.
;18. '~183' High-speed intake passage 17 with a larger cross-sectional area and lower intake resistance. ~17. ;17,'~17
Mainly distributed to 3', nozzles 38° to 383;
8. It is sucked into each cylinder 1 together with the injected fuel from ' to 383'.

As mentioned above, each high-speed intake passage is formed in a straight line, and its length is set to a length that maximizes the charging efficiency due to the intake inertia effect during a predetermined high-speed operation of the engine. Therefore, the intake inertia effect is effectively exhibited and the high-speed output performance of the engine can be fully satisfied.

Incidentally, in the present invention, a carburetor type can be adopted as the fuel supply method, and in this case, the throttle valve cylinder 32 is replaced with a carburetor, and the fuel injection nozzle 38. ~383;381'~
383' is to be removed.

As described above, according to the present invention, in a V-type multi-cylinder internal combustion engine having a pair of cylinder rows, the cylinders are connected to a plurality of intake boats of each cylinder row and are assembled in the valley between both cylinder rows,
and a plurality of independent high-speed intake passages linearly extending outward from the valley along the axis of the crankshaft, and an intake distribution chamber arranged in parallel with the valley and opening the entrance of each of the high-speed intake passages. , an intake manifold is constituted by a plurality of low-speed intake passages whose inlets are branched from branch ports provided in the middle of each of the high-speed intake passages and whose inlets open into the intake distribution chamber, and the length of each of the high-speed intake passages is determined by the length of each high-speed intake passage. , shorter than the total length of each of the corresponding low-speed intake passages and each of the high-speed intake passages downstream of the branch port;
An on-off valve is provided in each of the high-speed intake passages upstream from the branch port, and an actuator is connected to the on-off valve to open and close the on-off valve in response to a predetermined high-speed operating state of the engine. Therefore, the effective intake pipe length of the engine can be controlled in two stages by the opening and closing operation of the opening and closing valve, and by utilizing the intake inertia effect, the charging efficiency can be constantly increased and the output performance of the engine can be improved. Since the passage extends linearly along the axis of the crankshaft, when the engine is running at high speed, this high-speed intake passage effectively provides an intake inertia effect.
This allows the engine to fully demonstrate high output performance. Moreover, each intake passage is arranged by effectively utilizing the valley between both cylinder rows, and the intake air distribution chamber with a desired volume is restricted by the valley 7t1. Since these air intake passages and intake air distribution chambers are arranged without increasing the overall height of the engine, it is possible to contribute to making the engine more compact.

[Brief explanation of drawings]

The drawings show one embodiment of the present invention; FIG. 1 is a longitudinal sectional front view of the main parts of the entire engine, FIG. 1A is a bottom view of the cylinder head of the engine shown in FIG. 1, and FIG. Figure 3 is a side view of the intake manifold in Figure 1, Figures 4, 5 and 6 are IV-I in Figure 2.
V line, v-v line and VT-VI line sectional view, Figure 7 is the second
It is a sectional view taken along the line ■-■ in the figure. aI ~" 33 (1, '-(z 3/, ・Inlet end, "I ~ h33h, r ~ h31... Branch mouth, C',
ct...Left and right cylinder rows, AI...Intake manifold, V...Valley 1...Cylinder, 10...
Valve mechanism, 11... Intake valve, 12... Exhaust valve, 14
1-143;14. '~143'...Intake port,
16... Intake distribution chamber, 16a... Inlet thereof, 17.
~173; 171'~173'...high speed intake path, 18
1~IL) 181'~183'...Low speed intake path, 24
．． ~243;241'~243'...Opening/closing valve, 25
,．． 25□・・・1st. Second valve stem patent applicant Honda Motor Co., Ltd. 22-

Claims (1)

[Scope of Claims] (1) An intake system for a V-type multi-cylinder internal combustion engine in which a pair of cylinder rows each having a plurality of cylinders arranged in the axial direction of a crankshaft are arranged in a V-shape, a plurality of independent high-speed intake passages connected to the plurality of intake ports of each cylinder row, converging in the valley of both cylinder rows, and extending linearly outward from the valley along the axis of the crankshaft; an intake distribution chamber that is arranged in parallel in the valley and opens the entrance of each of the high-speed intake passages, and a plurality of air intake distribution chambers that branch from branch ports provided in the middle of each of the high-speed intake passages and that open into the intake distribution chambers. Constructs a low-speed intake passage and a better intake manifold,
The length of each of the high-speed intake passages is made shorter than the total length of each of the corresponding low-speed intake passages and each of the high-speed intake passages downstream of the branch port, and the length of each high-speed intake passage upstream of the branch port is An intake system for a V-type multi-cylinder internal combustion engine, comprising an on-off valve that opens and closes the on-off valve, and an actuator that opens and closes the on-off valve in response to a predetermined high-speed operating state of the engine. . (2. In the item described in claim (1),
V in which the plurality of high-speed intake passages are formed to have substantially the same length as each other;
Intake system for a multi-cylinder internal combustion engine. (3) Percentage Scope of Claims Paragraph (2),
An intake system for a V-type multi-cylinder internal combustion engine, wherein the lengths of entry ends of the high-speed intake passages into the intake distribution chamber are different from each other in order to make the plurality of high-speed intake passages substantially the same length. (4) In what is stated in claim (1),
The intake distribution chamber is defined in a cylindrical shape by the plurality of low-speed intake passages arranged surrounding it, and two cylinder rows closest to the intake distribution chamber are located at both ends of the cylindrical intake distribution chamber. An intake system for a V-type multi-cylinder internal combustion engine with two low-speed intake passages connected to the intake port.