WO2015163052A1 - Dispositif de refroidissement destiné à un moteur à combustion interne - Google Patents

Dispositif de refroidissement destiné à un moteur à combustion interne Download PDF

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Publication number
WO2015163052A1
WO2015163052A1 PCT/JP2015/058294 JP2015058294W WO2015163052A1 WO 2015163052 A1 WO2015163052 A1 WO 2015163052A1 JP 2015058294 W JP2015058294 W JP 2015058294W WO 2015163052 A1 WO2015163052 A1 WO 2015163052A1
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WIPO (PCT)
Prior art keywords
cooling device
container
exhaust
internal combustion
combustion engine
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PCT/JP2015/058294
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English (en)
Japanese (ja)
Inventor
正和 田畑
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トヨタ自動車株式会社
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Priority to JP2016514814A priority Critical patent/JPWO2015163052A1/ja
Publication of WO2015163052A1 publication Critical patent/WO2015163052A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the present invention relates to a cooling device for an internal combustion engine, and more particularly to a cooling device that cools exhaust gas that becomes high temperature under high load.
  • Patent Document 2 discloses that a bypass passage that bypasses the heat exchanger disposed in the exhaust passage is provided, and the exhaust gas path is switched between the heat exchanger and the bypass passage by a valve.
  • a valve that is exposed to high-temperature exhaust gas is required to have high heat resistance, but high cost is required to satisfy such a requirement.
  • the effect of lowering the temperature of the exhaust gas is increased as the load is higher, the cooling effect when the exhaust gas is passed through the heat exchanger becomes lower as the flow rate of the exhaust gas increases.
  • the present invention has been made in view of such problems, and an object of the present invention is to provide a cooling device having a self-adjusting function that automatically increases the cooling capacity in accordance with an increase in the load of the internal combustion engine. .
  • the cooling device includes a container having one gas inlet / outlet, a cooler core disposed inside the container, a branch from the exhaust passage in a section from the exhaust valve to the catalyst, and the exhaust passage and the inlet / outlet of the container. And a connecting pipe to be connected.
  • the shape of the container may be cylindrical, bag-like, or more complicated as long as there is only one gas inlet / outlet.
  • the cooler core is preferably a heat exchanger that cools the internal gas by heat exchange with other fluids.
  • the connecting pipe preferably branches from the exhaust passage in a section from the exhaust valve to the turbocharger turbine.
  • the container and the connecting pipe are configured to satisfy the following relationship.
  • the following relationship is a condition in which exhaust gas flows into the cooling space in the container through the connecting pipe due to pressure pulsation in the exhaust passage, and the replacement efficiency of the gas in the cooling space increases as the load increases.
  • the container and the connecting pipe are preferably such that the resonance frequency of the internal gas is greater than 0.5 times and less than 1.5 times the frequency of the pressure pulsation generated in the exhaust passage when the internal combustion engine outputs the maximum torque. Configured. This is a condition in which the resonance pressure in the container and the connecting pipe is synchronized with the pressure pulsation in the exhaust passage, and the inflow of exhaust gas into the cooling space and the exhaust of exhaust gas from the cooling space are efficiently repeated.
  • a marginal space is provided between the rear end surface of the cooler core and the container.
  • V3 the volume of the cooler core
  • V4 the volume of the extra space provided between the rear end face of the cooler core and the container
  • V4 the container and the connecting pipe are configured to satisfy the following relationship as well. Is more preferable.
  • the following relationship is a condition for exhaust gas to reach the interior of the container through the cooling space at a high load, that is, a condition that can further improve the efficiency of replacing the gas in the cooling space.
  • the exhaust gas flows into the container through the connecting pipe by the pressure pulsation in the exhaust passage, and the exhaust gas is cooled by the cooler core in the container.
  • the efficiency of gas replacement in the cooling space is low during low-load operation where the ratio between the minimum and maximum exhaust pressure is small, and increases as the ratio between the minimum and maximum exhaust pressure increases as the load increases. Go. That is, according to the cooling device according to the present invention, a self-adjusting function is realized in which the cooling capacity automatically increases as the load of the internal combustion engine increases.
  • FIG. 1 is a diagram showing an internal combustion engine 2 with a turbocharger provided with a cooling device 101 according to Embodiment 1 of the present invention.
  • the internal combustion engine 2 is a four-stroke one-cycle engine and is an in-line four-cylinder engine in which four cylinders are provided in series.
  • the internal combustion engine 2 may be configured as a spark ignition engine, or may be configured as a compression self-ignition engine.
  • the cylinder head 4 of the internal combustion engine 2 is formed with an intake port 8 and an exhaust port 10 leading to the combustion chamber 6.
  • An intake valve 12 is provided between the combustion chamber 6 and the intake port 8, and an exhaust valve 14 is provided between the combustion chamber 6 and the exhaust port 10.
  • An intake pipe 16 is connected to the intake port 8, and an exhaust pipe 24 is connected to the exhaust port 10.
  • the intake port 8 and the intake pipe 16 are combined to form an intake passage, and the exhaust port 10 and the exhaust pipe 24 are combined to form an exhaust passage.
  • a compressor 32 of a turbocharger 30 is attached to the intake pipe 16, and a turbine 34 of the turbocharger 30 is attached to the exhaust pipe 24.
  • An intercooler 20 is provided downstream of the compressor 32 in the intake pipe 16, and a throttle valve 18 is provided downstream of the intercooler 20.
  • a catalyst 26 for purifying the exhaust gas is provided downstream of the turbine 34 in the exhaust pipe 24.
  • the internal combustion engine 2 includes an actuator such as a fuel injection device, a variable valve timing mechanism, and an ignition device, and
  • the cooling device 101 of Embodiment 1 is attached upstream of the turbine 34 in the exhaust pipe 24.
  • the cooling device 101 includes a water-cooled cooler core (hereinafter, water-cooled cooler) 120.
  • FIG. 2 is a diagram showing in detail the mounting position of the cooling device 101 in the exhaust pipe 24.
  • the exhaust pipe 24 is attached to the cylinder head 4 and includes an exhaust manifold connected to the exhaust ports of the cylinders # 1, # 2, # 3, and # 4.
  • a hole 40 is formed in the junction where the four branch pipes of the exhaust manifold merge, and the cooling device 101 is attached to the hole 40.
  • FIG. 3 is a graph showing changes in the exhaust pipe pressure acting on the position of the hole 40 depending on the crank angle.
  • the exhaust pipe pressure shown in the graph is an absolute pressure.
  • changes in the exhaust pipe pressure under various intake pipe pressures pressures downstream of the throttle valve) are drawn with different line types.
  • the exhaust pipe pressure periodically increases and decreases. Since the internal combustion engine 2 is an in-line four-cylinder engine, the pulsation cycle of the exhaust pipe pressure is 180 degrees.
  • the exhaust pipe pressure changes from the lowest pressure to the highest pressure the exhaust gas flows into the cooling device 101 from the hole 40, and when the exhaust pipe pressure changes from the highest pressure to the lowest pressure, the cooling device 101 enters the hole 40. Exhaust gas is discharged.
  • the inflow amount and the exhaust amount of exhaust gas per cycle increase as the amplitude of the exhaust pipe pressure pulsation increases.
  • the minimum and maximum exhaust pipe pressures both increase as the intake pipe pressure increases, and the pulsation amplitude increases as the intake pipe pressure increases. Therefore, when the intake pipe pressure is the highest, the inflow amount and the exhaust amount per cycle of the exhaust gas are maximized, and the inflow amount and the exhaust amount decrease as the intake pipe pressure decreases.
  • FIG. 4 is a graph showing the change of the exhaust pipe pressure acting on the position of the hole 40 when the intake pipe pressure is the highest, depending on the crank angle. Since the intake pipe pressure is proportional to the air flow rate, this graph shows a change in the exhaust pipe pressure at the maximum load, that is, when the internal combustion engine 2 outputs the maximum torque. The magnitude of the torque output from the internal combustion engine 2 depends on the rotational speed of the internal combustion engine 2, but the maximum torque in this specification means the maximum torque at all the rotational speeds.
  • the maximum exhaust pipe pressure at the maximum torque is defined as “B”
  • the minimum exhaust pipe pressure at the maximum torque is defined as “C”.
  • the values of B and C are not obtained on-board, but are values obtained in advance in a test.
  • the ratio of C to B is defined as “A”.
  • a defined as above is the minimum value of the ratio of the minimum pressure to the maximum pressure of the exhaust pipe pressure.
  • the cooling device 101 according to the first embodiment is designed based on the value A.
  • FIG. 5 is a diagram showing details of the cooling device 101 of the first embodiment.
  • the cooling device 101 includes a container 112 including a water-cooled cooler 120 and a connection pipe 110 that branches from the exhaust pipe 24 at the hole 40 and connects the container 112 to the exhaust pipe 24.
  • the water cooling cooler 120 is a heat exchanger that cools the exhaust gas in the container 112 by heat exchange with cooling water.
  • the structure of the water-cooled cooler 120 is not limited, and for example, a structure used in an EGR cooler can be used.
  • a water supply pipe that supplies cooling water to the water-cooled cooler 120 and a drain pipe that discharges cooling water from the water-cooled cooler 120 are connected to the container 112, but these are not shown.
  • a margin space is provided between the cooling space cooled by the water-cooled cooler 120 and the container 112, but this margin space may not be provided.
  • the exhaust gas flowing through the exhaust pipe 24 is pushed into the connection pipe 110 by the pulsation of the pressure of the exhaust pipe 24 and further pushed into the container 112.
  • whether or not the exhaust gas reaches the cooling space cooled by the water-cooled cooler 120 depends on the relationship between the magnitude of the pulsation of the exhaust pipe pressure and the structure of the cooling device 101.
  • the volume from the position of the hole 40 that is the branch point of the connecting pipe 110 to the front end surface 122 of the water-cooled cooler 120 is “V1”
  • the volume of the container 112 on the back side from the front end surface 122 of the water-cooled cooler 120 is “V2”.
  • V2 includes the volume of the space in which the exhaust gas in the water-cooled cooler 120 flows (effective cooling volume), but does not include the volume of the portion of the water-cooled cooler 120 through which the cooling water flows.
  • V1 and V2 defined here and A defined earlier are used, the condition for the exhaust gas to reach the water-cooled cooler 120 is expressed by the following relational expression (1).
  • Equation (1) is a condition under which the exhaust gas can reach the water-cooled cooler 120 when the internal combustion engine 2 outputs the maximum torque. As the value on the left side is smaller than the value on the right side, the exhaust gas can reach deeper in the water-cooled cooler 120. The value on the right side is determined by the specifications of the internal combustion engine 2, and the value on the left side is determined by the structure of the cooling device 101. The cooling device 101 is configured so that the relationship of the expression (1) is satisfied.
  • FIG. 6 is a graph showing the effect obtained by configuring the cooling device 101 as described above.
  • the horizontal axis of the graph is the torque of the internal combustion engine 2, and the vertical axis is the outlet temperature of the turbine 34.
  • the temperature described as having a cooler in the graph is a temperature when the cooling device 101 is provided.
  • the temperature indicated as “no cooler” is a temperature when the cooling device 101 is not provided.
  • the exhaust gas does not reach the water-cooled cooler 120 or does not enter the water-cooled cooler 120 even if it reaches.
  • the exhaust gas enters into the water-cooled cooler 120.
  • the temperature fall of exhaust gas by cooling with the water cooling cooler 120 becomes large, so that the reach distance of the exhaust gas in the water cooling cooler 120 becomes long.
  • a cooling effect corresponding to the load as shown in the graph can be obtained.
  • the cooling device 101 of the first embodiment is provided with a self-adjusting function that automatically increases the cooling capacity when the load of the internal combustion engine 2 increases.
  • the exhaust gas temperature can be reduced to protect the exhaust system components.
  • the exhaust gas temperature is not unnecessarily lowered during low load operation, it is possible to prevent the acceleration response of the turbocharger 30 from deteriorating and the activation delay of the catalyst 26 at the start.
  • FIG. FIG. 7 is a diagram showing the turbocharged internal combustion engine 2 provided with the cooling device 102 according to the second embodiment of the present invention.
  • the cooling device 102 according to the second embodiment is configured by adding an expansion pipe 130 to the cooling device 101 according to the first embodiment.
  • FIG. 8 is a diagram showing details of the cooling device 102 according to the second embodiment.
  • the cooling device 102 according to the second embodiment includes a connection pipe 110, a container 112, and an expansion pipe 130.
  • the expansion tube 130 is attached to the side of the container 112 opposite to the side to which the connection tube 110 is connected.
  • the distal end (that is, the end opposite to the side attached to the container 112) 132 of the expansion tube 130 is closed.
  • one structure including the container 112 and the expansion tube 130 corresponds to the “container” in the present invention.
  • valves may be provided in the connecting pipe 110 and the extension pipe 130 to restrict the inflow of exhaust gas to these and the exhaust gas from them.
  • the volume of the margin space behind the water-cooled cooler 120 viewed from the hole 40 is increased. If the marginal space behind the water-cooled cooler 120 is large, the exhaust gas easily reaches the back of the water-cooled cooler 120 correspondingly. As the exhaust gas reaches deeper in the water-cooled cooler 120, the efficiency of replacing the gas in the water-cooled cooler 120 increases, and the cooling effect of the exhaust gas by the water-cooled cooler 120 increases.
  • the effective cooling volume of the water-cooled cooler 120 (the volume of the space in which the exhaust gas in the water-cooled cooler 120 circulates) is “V3”, and the volume of the marginal space from the rear end surface 124 of the water-cooled cooler 120 to the tip 132 of the expansion pipe 130. Is defined as “V4”.
  • V3 and V4 corresponds to V2 defined above.
  • V3 and V4 defined here and A and V1 defined above are used, the condition for the exhaust gas to reach the margin space behind the water-cooled cooler 120 is expressed by the following relational expression (2). (V1 + V3) / (V1 + V3 + V4) ⁇ 1-A (2)
  • Equation (2) is a condition that allows the exhaust gas to reach the marginal space behind the water-cooled cooler 120 when the internal combustion engine 2 outputs the maximum torque.
  • the exhaust gas can reach the back of the marginal space, that is, near the tip 132 of the expansion tube 130.
  • the value on the right side is determined by the specifications of the internal combustion engine 2
  • the value on the left side is determined by the structure of the cooling device 102.
  • the cooling device 102 is configured so that the relationship of the expression (2) is satisfied.
  • FIG. 9 is a diagram showing the pulsation of the pressure generated in the exhaust pipe 24 and the resonance of the air column in the cooling device 102 side by side.
  • the lower graph in FIG. 9 shows the change in turbine inlet pressure (exhaust pipe pressure) depending on the crank angle.
  • the resonance frequency is smaller than the frequency of the exhaust pipe pressure pulsation, that is, when one cycle of the exhaust pulsation is shorter than one wavelength of the vibrating air column (case 2), the exhaust pulsation peak and the resonance peak However, the resonance valley shifts to the retard side with respect to the exhaust pulsation valley.
  • the resonance valley overlaps the exhaust pulsation peak as in the case 2, the exhaust gas is hardly discharged from the cooling device 102 to the exhaust pipe 24. Therefore, in order for the exhaust gas to be discharged from the cooling device 102, it is necessary that a resonance valley has arrived before the exhaust pulsation peak arrives.
  • the resonance frequency needs to be larger than 1 ⁇ 2 times the pulsation frequency of the exhaust pipe pressure.
  • the resonance frequency is higher than the frequency of the exhaust pipe pressure pulsation, that is, when one cycle of the exhaust pulsation is longer than one wavelength of the vibrating air column (case 3), the exhaust pulsation peak and the resonance peak However, the resonance valley shifts to the advance side with respect to the exhaust pulsation valley. Even when the resonance valley overlaps the exhaust pulsation peak as in the case 3, the exhaust gas is hardly discharged from the cooling device 102 to the exhaust pipe 24. Therefore, in order for the exhaust gas to be discharged from the inside of the cooling device 102, it is necessary that the resonance valley arrive after the exhaust pulsation peak arrives. For this purpose, the resonance frequency needs to be smaller than 3/2 times the pulsation frequency of the exhaust pipe pressure.
  • the resonance frequency of the gas inside the cooling device 102 is greater than 0.5 times and less than 1.5 times the frequency of the pulsation of the exhaust pipe pressure when the internal combustion engine 2 outputs the maximum torque. desirable. This also applies to the cooling device 101 of the first embodiment. It is desirable that the shapes of the connecting pipe 110 and the container 112 are adjusted so that the above-described condition regarding the resonance frequency is satisfied.
  • the resonance frequency of the internal gas can be adjusted by the length of the expansion pipe 130.
  • FIG. 10 is a graph showing the relationship between the length of the expansion pipe 130, the temperature of the exhaust gas, and the resonance frequency of the gas inside the cooling device 102.
  • the temperature of the exhaust gas inside the cooling device 102 is cooled to about 100 ° C. by the cooling by the water cooling cooler 120. Therefore, assuming that the temperature of the exhaust gas is 100 ° C., the length of the expansion pipe 130 is determined so that the resonance frequency falls within the range of 0.5 to 1.5 times the pulsation frequency of the exhaust pipe pressure. Good. More preferably, the length of the expansion pipe 130 is set to the pulsation frequency of the exhaust pipe pressure as much as possible so that the resonance frequency is within the above-described desired range at the same time that the relationship of the expression (2) is satisfied. Adjusted to match.
  • FIG. 11 is a graph showing the relationship between the length of the expansion tube 130 and the cooling effect.
  • the cooling effect of the cooling device 102 that is, the amount of decrease in the temperature of the exhaust gas by the cooling device 102 becomes maximum when the length of the expansion pipe 130 is about 830 mm, and even if longer than that, Moreover, even if it is shorter than that, the cooling effect of the cooling device 102 is reduced. Therefore, in the example shown in this graph, it can be seen that 830 mm is the most desirable length of the expansion tube 130.
  • the length of 830 mm is a length that satisfies the relationship of the expression (2) and at the same time the resonance frequency falls within the range of 0.5 to 1.5 times the pulsation frequency of the exhaust pipe pressure.
  • the cooling device 102 of the second embodiment not only a self-adjusting function that automatically increases the cooling capacity when the load of the internal combustion engine 2 increases but also the cooling capacity of the water cooling cooler 120 is provided. Can be used more effectively.
  • FIG. FIG. 12 is a diagram showing the turbocharged internal combustion engine 2 provided with the cooling device 103 according to the third embodiment of the present invention.
  • the cooling device 103 according to the third embodiment includes an expansion container 140 having a throttle instead of the cylindrical expansion tube 130 provided in the cooling device 102 according to the second embodiment.
  • one structure including the container 112 and the expansion container 140 corresponds to the “container” in the present invention. If it is bowl-shaped like this expansion container 140, the volume of the extra space behind the water-cooled cooler 120, that is, V4 in equation (2) can be increased.
  • the resonance frequency of the gas inside the cooling device 103 can be adjusted by the volume of the expansion container 140 and the diameter of the throttle. Therefore, in the cooling device 103 of the third embodiment, the volume and throttle diameter of the expansion container 140 are adjusted so that the resonance frequency falls within the range of 0.5 to 1.5 times the pulsation frequency of the exhaust pipe pressure.
  • FIG. FIG. 13 is a diagram showing the turbocharged internal combustion engine 2 including the cooling device 104 according to the fourth embodiment of the present invention.
  • the cooling device 104 of the fourth embodiment has the same structure as the cooling device 103 of the third embodiment. However, while the cooling device 103 according to the third embodiment is connected to the exhaust pipe (more specifically, the collection portion of the exhaust manifold), the cooling device 104 according to the fourth embodiment is provided for each cylinder. Connected to the exhaust port 10. More specifically, a passage branched from the exhaust port 10 is formed in the cylinder head 4, and the cooling device 104 is attached to the passage. For this reason, only the pulsation of the pressure of the exhaust gas discharged from one cylinder acts on the cooling device 104.
  • the period of pressure pulsation is one cycle, that is, 720 degrees.
  • the resonance frequency of the gas inside the cooling device 104 falls within the range of 0.5 to 1.5 times the frequency of the pressure pulsation with respect to the pressure pulsation having a period of 720 degrees. In this way, the volume and the diameter of the expansion container 140 are adjusted. According to the cooling device 104 of the fourth embodiment, the temperature of the exhaust gas in the exhaust port 10 can be lowered to cool the exhaust valve 14 in a thermally severe environment.
  • FIG. FIG. 14 is a diagram showing the turbocharged internal combustion engine 2 including the cooling device 105 according to the fifth embodiment of the present invention.
  • the cooling device 105 of the fifth embodiment has the same structure as the cooling device 103 of the third embodiment. However, the cooling device 105 of the fifth embodiment is attached upstream of the wastegate valve 38 in the bypass passage 36 that bypasses the turbine 34.
  • the cooling device 105 according to the fifth embodiment is particularly provided for cooling the waste gate valve 38.
  • the bypass passage 36 to which the cooling device 105 is attached has the same pressure pulsation as that of the upstream exhaust pipe 24, but the exhaust gas flow rate is small. For this reason, according to the cooling device 105 of the fifth embodiment, a high cooling effect can be obtained for the exhaust gas flowing through the bypass passage 36.
  • FIG. FIG. 15 is a diagram showing the turbocharged internal combustion engine 2 provided with the cooling device 106 according to the sixth embodiment of the present invention.
  • the entire cooling device 106 according to the sixth embodiment is built in the cylinder head 4. Specifically, a passage branched from the exhaust port 10 is formed in the cylinder head 4, and the water-cooled cooler 120 is accommodated in the passage. Also in the sixth embodiment, the cooling device 106 is configured to satisfy at least the relationship of the expression (1). Further, a marginal space may be provided behind the water-cooled cooler 120 as in the embodiment 2-5.
  • the cooling device 106 according to the sixth embodiment can effectively cool the exhaust valve 14 as the cooling device 104 according to the fourth embodiment.
  • FIG. 16 is a diagram showing a naturally aspirated internal combustion engine 202 including the cooling device 107 according to the seventh embodiment of the present invention.
  • the mounting position of the cooling device 107 according to the seventh embodiment is the upstream of the catalyst 26 in the exhaust pipe 24, more specifically, the section from the exhaust manifold assembly to the catalyst 26.
  • the self-adjusting function of the cooling capacity of the cooling device 107 is also effective for the naturally aspirated internal combustion engine 202.
  • the cooling device 107 has the same structure as the cooling device 103 of the third embodiment, but has the same structure as the cooling device 101 of the first embodiment and the cooling device 102 of the second embodiment. It can also be taken. Further, as in the fourth and sixth embodiments, the cooling device 107 can be attached to the exhaust port for each cylinder.
  • FIG. 17 is a diagram illustrating a modification of the cooling device 103 according to the third embodiment.
  • a branch pipe 136 that branches from the expansion pipe 130 is provided.
  • the tip of the branch pipe 136 is closed.
  • the marginal space behind the water-cooled cooler 120 may have a complicated shape.
  • the EGR cooler of the EGR device can also be used as a cooling device. By closing the EGR valve, the EGR pipe can function like the expansion pipe of the third embodiment.
  • the cooling medium used in the cooling mechanism is not limited to cooling water.
  • a heat exchanger using air as a cooling medium can also be used as the cooler core.
  • forced cooling from the outside of the container by wind generated by a fan may be used, or natural cooling may be performed by diffusion of heat by a radiator.
  • condensed water may be generated as the exhaust gas is cooled. Therefore, although not shown in Embodiment 1-7, it is desirable that the cooling device is provided with a drainage facility (for example, a drainage pipe and a valve) that discharges condensed water to the outside.
  • a drainage facility for example, a drainage pipe and a valve
  • a drainage facility can be attached to the bottom of the container 112.
  • a drainage facility can be attached to the tip 132 of the expansion pipe 130.
  • a drainage facility can be attached to the bottom of the expansion container 140.
  • the cooling device according to the present invention can be applied not only to an in-line engine but also to other multi-cylinder engines such as a V-type engine and a horizontally opposed engine. Moreover, the cooling device according to the present invention can be applied to an engine that performs explosion at unequal intervals or a single cylinder engine. The cooling device according to the present invention can also be applied to a two-stroke one-cycle engine.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Supercharger (AREA)
  • Exhaust Gas After Treatment (AREA)

Abstract

Selon la présente invention, un dispositif de refroidissement est équipé : d'un récipient (112) ayant un port d'entrée ou de sortie de gaz ; d'un centre de refroidissement (120) disposé à l'intérieur du récipient (112) ; et d'un tuyau de raccordement (110) se ramifiant à partir d'un tuyau d'échappement dans une zone (24) située entre une soupape d'échappement et un catalyseur et reliant le tuyau d'échappement (24) à l'orifice d'entrée ou de sortie du récipient (112). Lorsque V1 est le volume de l'espace situé entre le point de ramification du tuyau de raccordement (110) et une surface d'extrémité avant (122) du centre de refroidissement (120) dans le récipient (112), V2 est le volume du récipient (112) au-delà de la surface d'extrémité avant (122) du centre de refroidissement (120) en tant que V2, et A est le rapport de la pression minimale et la pression maximale indiquées par la pression du gaz d'échappement lorsqu'un moteur à combustion interne produit son couple maximal, le récipient (112) et le tuyau de raccordement (110) sont formés de façon à satisfaire la relation suivante. V1/ (V1 + V2) < 1-A
PCT/JP2015/058294 2014-04-25 2015-03-19 Dispositif de refroidissement destiné à un moteur à combustion interne WO2015163052A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2019124203A (ja) * 2018-01-19 2019-07-25 株式会社Ｓｕｂａｒｕ 排気クーラ

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JP7075220B2 (ja) 2018-01-19 2022-05-25 株式会社Subaru 排気クーラ

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