JPH01280632A - Intake system for engine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION (Industrial Field of Application) The present invention relates to an intake system for an L-noise engine that improves the filling efficiency of intake air through a resonance effect.

(Prior Art) Various engine intake devices have been known in which the filling efficiency is enhanced by the dynamic effect of intake air. For example, in the device disclosed in Japanese Patent Publication No. 60-14169, in a multi-cylinder four-engine engine, the intake system is divided into two groups in which the cylinders in which the intake order is not consecutive are the same group. Each of the intake systems is configured to include a large-volume gathering section to which the upstream ends of independent intake passages (intake two bold branches) for each cylinder are connected, and a resonant passage extending upstream from the gathering section. , A switching device is provided in the collecting section to enable communication and disconnection of the intake system phase of the -1-registered group, and the upstream end of each resonance passage is connected to the first flow side collecting chamber. 10. When the switching device is in the state where the above-mentioned groups are mutually equal to m1IiL, the intake pressure wave that is counteracted by the Tsuchiura side condensation will blind the supercharging effect in the low speed range of the lower engine. If we set the natural frequency of the intake system between the above-mentioned flow-side set ``all'' and each intake bow 1 to 6, the switching device will be in the state of communicating the named intake passage. The reason for this is that in a relatively high speed range, the inertial supercharging effect of the above-mentioned independent intake passage causes a force wave to be reflected at the Tsuchiura end of the independent intake passage for each cylinder and acts at the end of intake. The shape of the independent intake passage is designed to achieve a supercharging effect (supercharging effect).

[Problem to be solved by the invention] When the ten-distribution intake system h' is used to obtain supercharging action in the high-speed range by the inertial effect of the independent intake passages for each cylinder, the high-speed range and However, it is necessary to have an inertial effect within the practical rotational speed range, so the tuned rotational speed in the intake passage should be [, 1, 1, lower than the maximum allowable rotational speed for]. Therefore, it is necessary to form the intake passage in a certain way. However, since an intake passage is provided for each cylinder, if each independent intake passage is formed to be long, it becomes difficult to make the intake system compact.

In addition, above J: Separate the sea urchin intake system into two glues 1 [
ti! due to the above-mentioned independent intake passage. In addition to the bamboo effect, we can also expect a resonance effect due to the vibration of pressure waves in the resonant system that includes the collective part of the independent intake passages of each group and the passage part that communicates with them on the upstream side. ft. If the intake passage is formed long, the length of the communication part between the cylinders will be extremely short in order to have a resonance effect in the high-speed range, and the effect of dividing the intake system into two groups will be weakened. , and the natural oscillation J number of the resonance system cannot be sufficiently increased because it is dominated by the natural frequency of the independent intake passage. For these reasons, none of the conventionally known motors has been able to effectively obtain a resonance effect, particularly near the maximum rotational speed of the engine.

The present invention addresses the above-mentioned details by shortening the independent intake passages for each cylinder and converting the intake system into one.
In particular, the T engine output can be increased due to the resonance effect in the high speed range near the maximum allowable rotation speed of the 2 I engine.
There is something that covers the engine's intake system.

[1ζth f stage to solve the problem]

In order to achieve the above object, the present invention divides the intake system of an engine into a plurality of groups in which cylinders that are not consecutive in the intake order are grouped into the same group, and creates independent intake passages for each cylinder in each group. Gather each group above and
The intake passage, the collecting part, and the passage part connected to each collecting part form a resonance system for each group. IR high rotation speed Nma
For x, -(0, 7Nmax <N r < 1, 2Nmax is set as (-).

[Effect]

With the above configuration, by setting the inertia synchronized rotation speed of the independent intake passage as described above, the independent intake passage becomes sufficient. In order not to rely on inertial effects, by setting the resonance tuning rotation speed Nr of the resonant system as described below, as will be detailed later, the maximum allowable rotation speed N max of one engine can be achieved. Resonant supercharging effect can be obtained in the high speed range.

〔Example〕

FIG. 1 shows an embodiment in which the device of the present invention is applied to a V-type six-cylinder engine. Three cylinders 3a, 3b, 3c are installed (pulled), and the other bank 2
Three cylinders 3d, 3e, and 3f, numbered 4, 5, and 6, are provided. Each of the cylinders 3a to 3t is provided with an intake boat 4a to 4f and an exhaust port 1- (not shown), and these boats are opened and closed at predetermined timings by intake valves and υ1 valves (not shown). be done. The intake order (ignition order) of each of the cylinders 3a to 3t is as follows: No. 1 cylinder 3a-)4 aroma B3d->No. 2 cylinder 3b->
The order is from No. 5 cylinder 3e to No. 3 cylinder 3cmvθ to No. M3f.

The intake system of this engine has t between cylinders where the intake order is not consecutive.
are divided into two groups that are the same group, that is, according to the above intake order, then each cylinder 3a...330 of one bank 2 is! 7. Inhalation order is consecutive,
1% intake for each cylinder 3d to 3fb of the other bank 2
are not consecutive - (, the intake system is -h's bank 1 side glue / (1st group) and the other bank 2 side group (
Each of the independent intake passages 5a to 5C for each cylinder connected to each intake boat 4a to 4C of the first group and each intake boat 1 to 1 of the second group The independent intake passages 5d to 5f for each cylinder connected to the respective cylinders 4d to 41- are collected in each group, that is, the upstream ends of the independent intake passages 5a to 5C are connected to the collecting part 6 on the first group side. In addition to being connected to
Each Tsuchiura end of the intake passages 5 d to 5 is connected to the collecting portion 7 on the second group side. A passage 8.9 constituting an upstream communication part is connected to each end of the grouped gathering parts 6, 7, and the passages 8.9 are communicated with each other at the upstream end. A downstream communication passage 11 is connected to the other end of each of the gathering parts 6 and 7, to which the common intake passage 10 is connected. In the J common intake passage 10, 1acry + 1 in the order of upstream or 1
2. l'771] - meter 13 + ll; cL hiss 1:
A one-way valve 14 is provided.

In this embodiment, independent intake passages 5a leading to each group
~5c, 5d ~51'o,''; and a passage 8°9.1 that constitutes a communication portion between the gathering portion 6.7 and each gathering portion 6,7;
The flow side communication path 11 constitutes a resonance system.

In this resonance system, the upstream communication passage 11 constituted by the passage 8.9 and the upstream communication passage 11 may be formed to have the same length; In order to know the length, the lengths of the communicating portions on both sides may be made different by 10. Furthermore, as shown in the figure, an on-off valve 15 that opens and closes according to the number of rotations of one carrot is provided in the flow-side communication passage 11, and the on-off valve 15 at the mouth closes the communication passage F. When asked, the resonant natural frequency of the resonant system changes.

Additionally, the ten-way gathering portion 6.7 may be formed of a pipe having the same cross-sectional area as the passage 8.9, but as shown in the figure, the cross-sectional area may be increased to provide a certain amount of capacity. However, you can still get the resonance effect.

Intake passages 5a to 5 enter this intake device.
r is the habitus [tuned rotation speed Ni is the maximum allowable engine speed (maximum allowable engine speed since engine reliability is zero) NIllaX, Ni>Nmax...
It is formed sufficiently short so that...■. In addition, the resonance tuning speed Nr due to the shortest path of the resonance system is
0, 7NnlaX for maximum rotational speed NmaX
<N r < 1, 2Nmax ++++++・■
The length, capacity, etc. of the parts that make up the resonance system are set so that 4T.

The 41 setting will be explained with reference to the model of the J intake system shown in FIG. The size of the independent intake passages 5a to 5f is ρ, the cross-sectional area of this passage is 1- (see Fig. 2), and the cylinder volume is vm. If A speed is expressed by a, crank angle is expressed, and I is expressed by O, then the independent intake passages 5a to 5 [tell
The tuning rotation speed N1 and the tuning frequency ν are as follows (■), (4)
Formula J, u';l 1. 'Niru.

N1=-0・ν/6 ・・・・・・■v= (a
/2π)Ewa 〒cho4■ ・・・・・・0120 type is,
It is obtained from the fact that the inertial tuning line f1 is (60/Ni)·(θ/360)=1/ν.

Therefore, by forming the independent intake passages 58 to 5f sufficiently short, the inertia tuning rotational speed N1 determined from the -20,0 formula can be increased to +Vj (14 times the condition of the 20 formula).

In addition, according to the model 1) shown in Fig. 2, the independent intake passages 5a-5G (5d to 5'l') and J of each group, as well as the convergence part 6 (7) and the communication part between them, are included. The resonant tuning rotational speed N r d-3J: and the resonant natural frequency νr of the L ringing system are
The next qD, J of the 0 formula, becomes.

Nr − (120/m)Xνr ・・・・・・■vr
-(a/4)X (1/ (Vr/F-+ l--N
')))...■ m: Number of cylinders in 1 group a: Sound velocity Vr: Capacity between independent intake passages in 1 group and the collecting part (shaded area in Figure 2) 1: Between the two collecting parts Average cross-sectional area of the communicating part [-20 midpoint of the communicating part'', length C' 1]: Average diameter of the communicating part (tube end correction), that is, the equivalent length of the resonant system is approximately (V
r/F+L+1), and since it is thought that the 11-negative part of the pressure wave is inverted and reflected at the midpoint of the above-mentioned communication part, two round trips of the pressure wave correspond to one cycle, so the resonance characteristic The vibration frequency vr can be approximately determined by formula 120. In addition, for each glue 1, the number of cylinders in one group m f is determined by two revolutions of the engine. The resonance tuning rotation speed Nr is determined by the above equation 0.

In this way, the resonance tuning rotation speed Nr is determined by the specifications of the resonance system, such as the capacitance Vr, the average cross-sectional area, the length 1-, and the average diameter. Therefore, if the resonant tuning rotation speed Nr when the jt ringing system is on the highest path is within the range of the above equation 0, then the specifications of the resonant system are set, for example as shown in Fig. In the structure, each independent intake passage 58 to 5', convergence part 6, 7, passage 8 constituting a resonance system
, 9, the specifications of the method side communication path 11, etc. are set as shown in L.

According to this J, Eel intake system, the resonance system is constructed by dividing the intake system into two groups in which cylinders whose intake order is not consecutive are assigned the same group 1. Pressure waves generated by cylinder operation propagate from the independent intake passages 58 to 5c, 5d to 5f to the collecting portions 6 and 7i15 and the communication portion between the collecting portions 6 and 7, and pressure is applied to the parts that constitute these resonance systems. Vibration occurs. Then, the resonance natural frequency νr is 16 for each group.
When the number of intakes matches the number of intakes, the 1i force wave generated in each cylinder of the same group resonates, and the state where the stupid vibration is strongest is reached. In this state, a supercharging effect due to the resonance effect is obtained in the rotation speed range near the resonance tuned rotation speed N, and the engine output is increased.

Dokuni, the shortest path of the resonance system is J, RuJ (sound tuning rotation speed N
r to the maximum allowable rotation speed Nmax of the engine.
By setting within the range of the formula, the engine output can be increased by resonance supercharging in the high speed range near the maximum allowable rotation speed Nmax (;j.
, I will explain.

Figure 3 shows a structure similar to that shown in Figure 1 when the resonance tuning rotation speed Nr is set to the divine value (ll'1).
] Characteristics of engine output torque (A1・~A5), both pJ
4 effects are shown in comparison with ↑ (1 (line B)) of a lifting platform that does not have an impact. In this figure, line 1 is the resonance tuning rotation speed Nr, which is the engine's maximum rotation speed N max. In this case, the maximum allowable rotation speed N max
Soil engine output! The output power is increased by 1-lux in the high-speed range near the 41st and 41st peaks. Also, [0,7
If Nmax < Nr < 1.2Nmax l, the resonance tuning rotation speed N1 is the above-mentioned maximum allowable rotation speed N max
Even if the platform is shifted (lines △2, A3), the peak J of the C1 engine output torque near the maximum rotational speed Nmax is still low and small, but it is sufficiently higher than when there is no resonance effect. Become. However, within the above range
Resonant synchronized rotation on the low speed side -'+3- Although the number Nr is off, the maximum rotation speed N old + x (,
If the carrot output 1 to 1 near 1 does not have a resonance effect, J will decrease and have the opposite effect (line △4), and the resonance synchronized rotation will be [greater on the high speed side than the stated range]. Number N"
When the above-mentioned allowable rotation speed is below Nmax, the difference in engine output from 1 to 100 kW or lυ, which does not affect the resonance effect, becomes 1.r (line △5). Therefore, the resonance tuning speed Nr is within the range specified by P. By setting J: to 1, the engine output 1 to 1 torque is increased in the high speed range near the maximum rotational speed Nm2+x.

In this case, by setting the inertia-tuned rotation speed Ni by the independent intake passages 58 to 5t as in the above equation 0, the resonance-tuned rotation speed Nr can be set without being controlled by the inertia-tuned rotation speed N1. By knowing the independent intake passages 5a to 51' in this way, it is possible to have a certain length in the communicating part between the gathering parts 6 and 7.
It is possible to increase the synchronized rotational speed Nr to the range specified by F, and the effectiveness of dividing the intake system into two groups is not impaired, and resonance at high speeds is effectively achieved. In addition, as mentioned above, the downstream side communication passage 11 (the on-off valve 15 is installed), and the resonant natural frequency changes depending on the opening and closing of the downstream communication passage 11.
It is possible to create resonance effects in different rotation speed ranges.

Note that the specific construction of the device of the present invention is not limited to the above-mentioned embodiments, but can be implemented in various ways, some examples of which are shown in FIGS. 4 to 7.

In one embodiment shown in FIG. 4, nine intake passages 58 to 50 on one bank 1 side of a V-type six-cylinder T-engine and each independent intake passages 56 to 51 on the other bank 2 side are assembled together. , connected to one end side of each of the collecting parts 16 and 17, and 7ζ
The passage 18.19 is communicated with the first flow end side and the supply intake passage 10 is connected to this part, and the F passage 18.1
9 JT flow end side communication point J, rim Tsuchiura (inner passage 18
．． 19 is installed. This communication portion 21 is provided with an on-off valve 22 that opens and closes in response to the engine speed t. Further, the communication portions 21, J:F flow side portions of the passages 18°-11) to 19 have a large cross-sectional area.

In the embodiment of the mouth, each independent intake passage 5a□51'L
In addition to setting the inertia-tuned rotation speed Ni as shown in the formula (2), the resonance-tuned rotation speed (resonance-tuned rotation speed when the on-off valve 22 is open) due to the shortest path passing through the communication portion 21 is set.
By setting Nr to J in the above-mentioned formula 0, a resonant supercharging effect can be obtained in the high speed range, similar to the embodiment shown in FIG. In this case, as the average cross-sectional area F in the formula 0 increases, the resonance natural frequency ν' increases, so the communication portion 21
The cross-sectional area of the passage on the downstream side should be made larger (this allows the communication part between the gathering parts to have a certain length, and the intake system should be divided into two groups (J
, while still being effective (this allows for a resonance effect in the high-speed range).

Figure 5) shows an embodiment in which the present invention is applied to a V-type 4-cylinder J-engine. In this case, -h cylinder 33a of bank 31
, 33b same 1, and cylinder 33c of the other bank 32,
In 33d and t, the intake system is not consecutive, so the intake system is divided into one bank 31 side group and the other bank 32 side group+'lJ'c, and 1A intake for each group. Passageway 35a.

While collecting 35 b, 35G, and 35d,
Gathering section 36.37. Passages 38, 39, common intake passage 40
, the downstream side communication passage 41, the on-off valve 45, etc. are constructed in the same manner as in the embodiment shown in FIG. Alternatively, a J resonance system may be configured as in the embodiment shown in FIG.

Furthermore, in the embodiment shown in FIG. 6, passages 58 and 59 are respectively connected to the gathering parts 56 and 57 of each group IO divided into one bank 1 side and the other bank 2 side. A common intake passage 60 is connected to the communication point on the flow end side of each of the passages 558 and 59, and passage-like portions 61 and 62 are provided which branch off from the midpoint of each of the passages 558 and 59, respectively. The ends of the passage-like portions 61, 62 are closed ends.

According to this embodiment, since the passage-like portions 61 and 62 are related to the natural frequency vl of the Jt sound as a part of the resonance system, the passage-like portions 6'l and 62 also contribute to the resonant tuning rotational speed. Nr can be adjusted. And in this case too, the above ■
, the independent intake passage 5 a-5) f so as to satisfy the formula
By setting up a resonance system, resonance supercharging can be effectively obtained in the high speed range near the maximum allowable rotation speed Nn1ax.

Figure 7 shows the case where it is applied to an in-line four-cylinder engine.1.
In this case, the number 1 cylinder 73 whose intake %l'l order is not consecutive
a and the fourth cylinder 73d are in the first group, and the second cylinder 73b
and No. 3 cylinder 73G are set as a second group, and each of the 1'J intake passages 75a, 75d and 75b, 75G are collected in each group, and each collecting portion 7
A common intake passage 80 is connected to the upstream end communication point of the passage 78 and 79 connected to the passage 78 and 77. Salary! A g pi system is constructed such that I II+ is obtained,
For example, passage-like portions ε3 and 82 branching from the passages 78 and 79, respectively, are installed. This passage-like portion 81.
82 may have a right end shape like the embodiment shown in FIG. J to open and close it,
It would be better to make it possible to change the resonance natural frequency. As in the other embodiments, the independent intake passages 73a to 73f and the resonance system are set to satisfy equations (1) and (2) above.

〔Effect of the invention〕

As described above, the present invention collects independent intake passages for each cylinder for each group in which cylinders whose intake order is not consecutive are grouped into the same group, and connects these and the passage portions connected to each collection part. A resonance system is configured, and - the inertial tuning rotation speed N1J5 due to the independent intake passage and the resonance tuning rotation speed Nr due to the shortest path of the resonance system are respectively Ni>Nmax Q, 7Nmax with respect to the maximum rotation speed Nmax of the engine. <Nr〆:l, 2Nmax is set so that the independent intake passages for each cylinder can be fully understood and the intake system can be made more compact, and the engine's In the high-speed range near the SKI rotary speed, the engine output can be increased by increasing the right gear J (11, Ningei Song (1111~)).

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram of an intake device 6 showing an embodiment of the present invention, FIG. 2 is an explanatory diagram showing a model of the intake device to explain the setting conditions of the independent intake passage and resonance system, and FIG. 33 7A and 7B are characteristic diagrams of one carrot output torque when the resonance tuning rotational speed is variously changed, and FIGS. 4 to 7 [j] are schematic diagrams of intake devices showing different embodiments. 3 a-3f, 33 a to 33 d, 73 a
~73 d...Cylinder, 5a ~riI', 35a~3
5d, 75a to 75d...Independent intake passage, 6.7.1
6, 17, 36.37, 56, 57.76.77...
Gathering part, 8.9.11.18.19.21.38,39
．． 41°58.59, 61, 62, 78.79.81.
82...A passageway connected to the gathering area.

Claims (1)

[Scope of Claims] 1. The intake system of the engine is divided into a plurality of groups in which cylinders whose intake order is not consecutive are grouped into the same group, and the independent intake passages for each cylinder are assembled in each group, and each of the above groups The independent intake passages and the collecting parts and the passage parts connected to each collecting part constitute a resonance system for each group, and the independent intake passages have an inertial tuned rotation speed that is higher than the maximum allowable rotation speed of the engine. and the resonance system is set so that the resonance tuning speed Nr of the shortest path satisfies 0.7Nmax<Nr<1.2Nmax with respect to the maximum allowable engine speed Nmax. The intake system of the engine.