JP2016138454A - Cooling device for engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce a load on each motor pump provided in a cooling water circulation passage for a heater core, thereby reducing the power consumption of the pump and improving the life thereof.SOLUTION: A cooling device for an engine includes a first circulation passage passing through a predetermined site in a cylinder head and the heater core, a second circulation passage passing through the other site in the cylinder head and auxiliary equipment, a motor-driven first pump provided in the first circulation passage for forcibly feeding cooling water, a second pump provided in the second circulation passage for forcibly feeding the cooling water, a first communication flow path for linking a downstream side portion of the auxiliary equipment in the second circulation passage to the first circulation passage, a second communication flow path for linking an upstream side portion of the auxiliary equipment in the second circulation passage to the first circulation passage, and a flow path switching valve for opening the first communication flow path and the second communication flow path. The flow path switching valve closes the first and second communication flow paths when a detected temperature is within a first temperature range during the warming-up of the engine, and opens the first and second communication flow paths when the detected temperature is within a second temperature range higher than the first temperature range.SELECTED DRAWING: Figure 8

Description

  The present invention relates to an engine cooling apparatus.

  2. Description of the Related Art Conventionally, an engine cooling device is known in which circulation of cooling water is limited during warm-up in order to promote engine warm-up (see, for example, Patent Document 1).

  The engine cooling device described in Patent Document 1 guides cooling water derived from the cylinder head of the engine to an air / liquid heat exchanger (radiator), and supplies the cooling water derived from the air / liquid heat exchanger to the cylinder head. Cooling circuit to be returned to the cooling circuit, a mechanical pump provided in the cooling circuit, and a downstream end connected between the air / liquid heat exchanger and the mechanical pump in the cooling circuit, and the cooling water derived from the cylinder head of the engine To the exhaust gas recirculation cooler, the passenger compartment heat exchanger (heater core), and the engine oil cooler in this order, and the heating circuit for returning the cooling water derived from the engine oil cooler to the cylinder head and the heating circuit An electric pump provided, and a mechanical pump and a control device for controlling the electric pump are provided.

  When the engine is cold, the control device performs control to stop the mechanical pump and drive the electric pump. Thereby, warm-up of a heater core and an engine can be promoted. As the engine warms up, the control device performs control to drive the mechanical pump and the electric pump. Thereby, cooling of an engine can be accelerated | stimulated, promoting warming-up of a heater core.

JP-T-2006-528297

  However, in the cooling device described in Patent Document 1, a passenger compartment heat exchanger and an auxiliary device (exhaust gas recirculation cooler and engine oil cooler) are arranged in the heating circuit. And the flow rate of the cooling water supplied to the auxiliary machine becomes the same. Since the required cooling water flow rate is often different between the passenger compartment heat exchanger and the auxiliary machine, it may not be preferable to provide the passenger room heat exchanger and the auxiliary machine in the same cooling water circuit.

  In order to eliminate such inconvenience, the downstream end of the heating circuit is directly connected to the cylinder head, only the passenger compartment heat exchanger and the electric pump are provided in the heating circuit, and the air / liquid heat exchanger is provided in the cooling circuit, By providing an auxiliary machine and a mechanical pump, it is conceivable to supply cooling water to the passenger compartment heat exchanger and the auxiliary machine through separate paths.

  However, when such a configuration is adopted, it is necessary to always drive the electric pump in order to promote warm-up of the passenger compartment heat exchanger, and power consumption by the electric pump increases. There is a risk of deteriorating the electric pump. In particular, when a small electric pump is used in order to reduce the manufacturing cost and make the electric pump more compact, the tendency becomes stronger.

  The present invention has been made in view of the above circumstances, and is provided in a cooling water circulation path for a heater core in a cooling water circulation system in which a cooling water circulation path for a heater core and a cooling water circulation path for an accessory are separately provided. Another object of the present invention is to provide an engine cooling device capable of reducing power consumption and improving the life of the pump by reducing the load applied to the electric pump.

  In order to solve the above problems, the present invention provides a first circulation path through which cooling water circulates through a predetermined portion in a cylinder head and a heater core of an air conditioner, and a cylinder head other than the predetermined portion. A second circulation path through which cooling water circulates through an inner part and an auxiliary machine outside the cylinder head, temperature detection means for detecting the temperature of the engine, and the first circulation path, An electric first pump that pumps cooling water, a second pump that is provided in the second circulation path and operates by receiving engine power, and pumps cooling water, and the second circulation A first communication flow path connecting the downstream part of the auxiliary machine in the path and the first circulation path; an upstream part of the auxiliary machine in the second circulation path; and the first circulation path. And a second communication channel connecting the first communication channel and the first communication channel A flow path switching valve that opens and closes the path and opens and closes the second communication flow path, and a controller that controls the operation of the flow path switching valve based on the detection result of the temperature detection means The control unit closes the first and second communication flow paths when the temperature detected by the temperature detection means is in the first temperature range during engine warm-up. When the temperature detected by the temperature detecting means is in a second temperature range higher than the first temperature range, (ii) control for opening the first and second communication flow paths is performed. An engine cooling device is provided.

  According to the present invention, in the control (i), the cooling water heated by the cylinder head is supplied to the heater core by the pumping force of the first pump, and in the control (ii), the cooling water heated by the cylinder head is The cooling water circulation system in which the cooling water circulation path (first circulation path) for the heater core and the cooling water circulation path (second circulation path) for the auxiliary machine are separately provided because the pressure is supplied to the heater core by the pumping force of the pump 2. , The load applied to the electric pump (first pump) provided in the cooling water circulation path (first circulation path) for the heater core can be reduced, and the power consumption and the life of the electric pump can be reduced. it can.

  That is, since the heater core is in a low temperature state at the initial stage of warm-up, control (i) for closing the first and second communication channels is performed. In this control, the cooling water heated by the cylinder head is supplied to the heater core by the pumping force of the first pump. In addition, since the first and second communication flow paths are closed and the first circulation path and the second circulation path are independent, the low-temperature cooling water in the second circulation path flows into the heater core. do not do. As a result, the temperature rise of the heater core is promoted.

  As the warm-up progresses, the temperature of the auxiliary device has risen sufficiently, so that control (ii) is performed to open the first and second connecting flow paths. In the state where the second pump is driven by the power of the engine, the upstream side portion of the auxiliary machine in the second circulation path has a higher coolant pressure than the downstream side part of the auxiliary machine. In the circulation path, a pressure difference is generated between the connection site with the first communication channel and the connection site with the second communication channel. Therefore, the cooling water can be circulated in the first circulation path using the pumping force of the second pump, and as a result, the load applied to the first pump provided in the first circulation path is reduced. can do. Therefore, it is possible to suppress the rotational speed of the first pump (including stopping the first pump).

  That is, by the control (ii), by generating a pressure difference by the second pump between two points distant from each other in the first circulation path, the first circulation path is utilized by utilizing the pumping force of the second pump. The cooling water is circulated, and as a result, the load applied to the first pump can be reduced, and the power consumption of the first pump can be reduced and the life can be improved. The control (ii) may be started between the late stage of warm-up and the completion of warm-up, or may be started after completion of warm-up.

  In the present invention, the second circulation path includes an accessory-side passage that passes through the accessory, and a radiator-side passage that is connected in parallel to the accessory-side passage and passes through the radiator. The flow path switching valve further performs opening and closing of the auxiliary machine side flow path and opening and closing of the radiator side flow path, and the control unit performs the radiator side flow in the control of (ii). (Iii) when the temperature detected by the temperature detection means is in a third temperature range higher than the second temperature range; It is preferable to perform control to open the auxiliary machine side flow path, the radiator side flow path, the first communication flow path, and the second communication flow path.

  According to this configuration, the cooling water can be cooled by the radiator after the warm-up is completed.

  In the present invention, the second circulation path includes an accessory-side passage that passes through the accessory, and a radiator-side passage that is connected in parallel to the accessory-side passage and passes through the radiator. The flow path switching valve further performs opening and closing of the auxiliary machine side flow path and opening and closing of the radiator side flow path, and the control unit performs the radiator side flow in the control of (ii). (Iii) when the temperature detected by the temperature detection means is in a third temperature range higher than the second temperature range; It is preferable to perform control to close the first communication flow path and open the auxiliary machine flow path, the radiator side flow path, and the second communication flow path.

  According to this configuration, it is possible to increase the cooling capacity of the cooling device by increasing the amount of cooling water that passes through the auxiliary machine and the radiator after the warm-up is completed. That is, in a state where the first communication flow path is opened, a part of the cooling water discharged from the first pump flows downstream without passing through the auxiliary machine and the radiator. Although the performance may be reduced, in the state where the first communication channel is closed, most of the cooling water discharged from the first pump flows via the auxiliary machine or the radiator, so that the cooling performance is reduced. Can be suppressed.

  In the present invention, the control unit further controls the discharge amount of the first pump based on the detection result of the temperature detecting means. In the control of (iii), the control units (i) and (ii) It is preferable to increase the discharge amount of the first pump rather than the above control.

  According to this configuration, by increasing the discharge amount of the first pump, the amount of cooling water flowing through the auxiliary machine and the amount of cooling water flowing through the radiator increase, so that the cooling performance of the cooling device can be improved. .

  In the present invention, in the control of (iii), the control unit increases the discharge amount of the first pump to the maximum discharge amount allowed for the first pump or near the maximum discharge amount. Is preferred.

  According to this configuration, since the amount of cooling water flowing through the auxiliary machine and the amount of cooling water flowing through the radiator are further increased, the cooling performance of the cooling device can be further improved.

  In the present invention, the predetermined part in the cylinder head is preferably an exhaust port side portion of the cylinder head.

  According to this configuration, warming up of the heater core can be promoted. That is, since the high-temperature exhaust gas flows through the exhaust port, the cooling water flowing through the exhaust port side portion of the cylinder head is quickly warmed to a high temperature. Therefore, the heat from the exhaust port side portion of the cylinder head is applied to the heater core, and the temperature rise of the heater core is promoted.

  In the present invention, a partition wall is provided between the exhaust port side portion of the cylinder head and a portion other than the exhaust port side of the cylinder head, and the exhaust port side portion and the exhaust port side other than the exhaust port side via the partition wall. These parts are preferably formed separately from each other.

  According to this configuration, the heat at the exhaust port side portion of the cylinder head can be preferentially used for the temperature rise of the heater core, and the temperature rise of the heater core is further promoted.

  In this invention, the said control part further controls the operating state of the said 1st pump based on the detection result of the said temperature detection means, and stops the said 1st pump in the control of said (ii). It is preferable.

  According to this configuration, since the first pump is stopped, it is possible to promote reduction in power consumption and improvement in life of the first pump.

  As described above, according to the present invention, in the cooling water circulation system in which the cooling water circulation path for the heater core and the cooling water circulation path for the auxiliary machine are separately provided, the load applied to the pump provided in the cooling water path for the heater core is reduced. By reducing, it is possible to reduce the power consumption and improve the life of the pump.

It is a block diagram which shows the whole structure of the cooling device of the engine which concerns on embodiment of this invention, and when the temperature of cooling water is less than T0, the state (water stop state) which stopped the flow of cooling water with the whole cooling device ). (A) is an expanded view of the surrounding wall of the rotary valve in the control state shown in FIG. 1, (b) is a figure which shows the position of the opening part provided in the housing surrounding a rotary valve. It is a block diagram which shows the whole structure of the cooling device of the engine which concerns on embodiment of this invention, and is a figure which shows the control state (control state A) when a combustion chamber wall temperature is more than T0 and less than T1. It is a block diagram which shows the whole structure of the cooling device of the engine which concerns on embodiment of this invention, and is a figure which shows the control state (control state B) when a combustion chamber wall temperature is more than T1 and less than T2. It is an expanded view of the surrounding wall of the rotary valve in the control state shown in FIG. It is a block diagram which shows the whole structure of the cooling device of the engine which concerns on embodiment of this invention, and is a figure which shows the control state (control state C) when a combustion chamber wall temperature is more than T2 and less than T3. It is an expanded view of the surrounding wall of the rotary valve in the control state shown in FIG. It is a block diagram which shows the whole structure of the cooling device of the engine which concerns on embodiment of this invention, and is a figure which shows the control state (control state D) when a combustion chamber wall temperature is more than T3 and less than T4. It is an expanded view of the surrounding wall of the rotary valve in the control state shown in FIG. It is a block diagram which shows the whole structure of the engine cooling device which concerns on embodiment of this invention, and is a figure which shows the control state (control state E) when a combustion chamber wall temperature is T4 or more and an engine load is less than predetermined value It is. It is an expanded view of the surrounding wall of the rotary valve in the operation state shown in FIG. It is a block diagram which shows the whole structure of the cooling device of the engine which concerns on embodiment of this invention, and is a figure which shows the control state (control state F) when a combustion chamber wall temperature is T4 or more and an engine load is more than predetermined value It is. It is an expanded view of the surrounding wall of the rotary valve in the operation state shown in FIG. It is a flowchart which shows the control action by ECU in embodiment of this invention. It is a flowchart which shows the control action by ECU in embodiment of this invention.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings.

  As shown in FIG. 1, the engine 5 in the present embodiment includes a cylinder block 5B and a cylinder head 5A provided on the upper side of the cylinder block 5B.

  FIG. 1 shows the cylinder head 5A as viewed from above, and the cylinder block 5B as viewed from the intake side.

  1, 3, 4, 6, 8, 10, and 12, when an arrow is described in the flow path of the cooling water, it indicates that the cooling water is flowing through the flow path, When an arrow is not described in this, it means that cooling water is not flowing through the flow path.

  A plurality of cylinders # 1 to # 4 into which pistons (not shown) are respectively inserted are formed in the cylinder head 5A and the cylinder block 5B. Specifically, a first cylinder # 1, a second cylinder # 2, a third cylinder # 3, and a fourth cylinder # 4 are formed in order from the left in FIG. The engine 5 is an in-line four-cylinder engine in which four cylinders # 1 to # 4 are arranged in series in the crankshaft direction. A rotary valve device 2 described later is provided at the end of the cylinder head 5A on the fourth cylinder # 4 side. The engine 5 is disposed in an engine room provided in the front part of the vehicle.

  A combustion chamber is formed above the piston. The cylinder head 5A is formed with an intake port and an exhaust port (both not shown) that open toward the combustion chamber. The intake port is located below the cylinders # 1 to # 4 in FIG. 1, and the exhaust port is located above the cylinders # 1 to # 4 in FIG. The intake port is for introducing intake air into each cylinder. The exhaust port is for exhausting exhaust from each cylinder.

  The cylinder head 5A is formed with an exhaust water jacket and a main water jacket. The exhaust-side water jacket passes through the portion on the exhaust port side of the cylinder head 5A from the first cylinder # 1 side to the fourth cylinder # 4 side in the cylinder row direction. The main water jacket has a portion other than a portion on the exhaust port side of the cylinder head 5A, that is, a portion around the combustion chamber and a portion on the intake port side in the cylinder row direction from the first cylinder # 1 side to the fourth cylinder # 4 side. pass.

  The exhaust side water jacket corresponds to an exhaust side flow path 22 (see FIG. 1) described later. The main water jacket corresponds to a main flow path 23 (see FIG. 1) described later. A partition wall 28 is provided between the exhaust side water jacket (exhaust side channel 22) and the main water jacket (main channel 23), and the exhaust side water jacket and the main water jacket are separated from each other via the partition wall 28. Is formed.

  The cylinder block 5B has a main water jacket provided around the cylinders # 1 to # 4. The main water jacket passes through the cylinder block 5B so as to go round from the first cylinder # 1 side to the fourth cylinder # 4 side to the first cylinder # 1 side. The water jacket of the cylinder block 5B corresponds to a block-side flow path 25 (see FIG. 1) described later.

  Next, the cooling device 1 for the engine 5 will be described in detail.

  As shown in FIG. 1, the cooling device 1 includes a heater circulation path 40, an auxiliary machine circulation path 41, a communication flow path 27, a communication flow path 45 (see FIG. 8), and water temperature sensors 7 and 8. , 24, accelerator opening sensor 30, crank angle sensor 32, intake air temperature sensor 38, heater side pump 4, auxiliary machine side pump 3, rotary valve device 2, and ECU 31 (Electronic Control Unit). I have.

  The heater side pump 4 is an electronically controlled electric pump. The heater-side pump 4 corresponds to the “first pump” in the present invention. The heater side pump 4 has one suction port and one discharge port. A downstream end of a heater-side flow path 15 described later is connected to the suction port. A branch pipe (not shown) that branches into two on the downstream side is connected to the discharge port. An upstream end of a communication channel 26 (see FIG. 1), which will be described later, is connected to one end of the branch pipe which is branched, and an upstream of an ETB-side channel 19 (see FIG. 1), which will be described later, is connected to the other end. The ends are connected.

  The auxiliary machine side pump 3 is a mechanical pump and operates by receiving the driving force of the engine. The auxiliary pump 3 corresponds to the “second pump” in the present invention.

  The auxiliary machine in this embodiment includes an EGR (Exhaust Gas Recirculation) cooler 9, an oil cooler 10, an EGR valve 11, an ATF (Automatic Transmission Fluid) warmer 12, an electronically controlled throttle body (hereinafter referred to as "ETB") 13, and This is a radiator 14.

<Configuration of Heater Circulation Path 40>
The heater circulation path 40 (see FIG. 1) is a path through which the cooling water circulates. The exhaust side flow path 22, the heater side flow path 15, the ETB side flow path 19, the flow path in the rotary valve device 2, and the communication. A flow path 26 is provided. The heater circulation path 40 corresponds to the “first circulation path” in the present invention.

  The exhaust side flow path 22 is a passage that passes through the exhaust port side portion 5a of the cylinder head 5A. One end of the exhaust side flow path 22 is connected to the block side flow path 25, and more specifically, is connected to a portion of the block side flow path 25 opposite to the rotary valve device 2. The other end of the exhaust side flow path 22 is connected to the rotary valve device 2.

  The heater side flow path 15 is a flow path that passes through the heater core 6 of the air conditioner. The upstream end portion of the heater-side flow channel 15 is connected to a midway portion of the exhaust-side flow channel 22, more specifically, a portion of the exhaust-side flow channel 22 opposite to the rotary valve device 2. A water temperature sensor 7 for detecting the temperature of the cooling water is provided downstream of the heater core 6 in the heater side flow path 15.

  The ETB side channel 19 is a channel that passes through the ETB 13. The downstream end of the ETB side channel 19 is connected to a section between the heater core 6 and the heater side pump 4 in the heater side channel 15.

  The communication channel 26 is a channel that connects the discharge port of the heater-side pump 4 and the rotary valve device 2. The downstream end portion of the communication flow path 26 is connected to a flow rate adjusting valve V3 (described later) in the rotary valve device 2.

<Configuration of rotary valve device 2>
As shown in FIG. 2 (b), the rotary valve device 2 includes a cylindrical rotary valve 2a, a rectangular parallelepiped housing 2b that houses the rotary valve 2a, and an electronically controlled electric motor that rotationally drives the rotary valve 2a. A motor (not shown). The rotary valve 2a is rotatable in the circumferential direction (axial direction) within the housing 2b.

  FIG. 2A is a development view of the rotary valve 2a in which the position on the circumferential surface of the rotary valve 2a is represented by an angle 0 ° to 360 ° around the axis of the rotary valve 2a. 2A is the axial direction of the rotary valve 2a, and the left-right direction in FIG. 2A is the circumferential direction of the rotary valve 2a.

  The rotary valve 2a sandwiches the partition wall W with a disk-shaped partition wall W (see FIG. 2 (a)) provided in the central portion in the axial direction, a solid cylindrical portion 21a provided on one side of the partition wall W. And a hollow cylindrical portion 22a provided on the other side. The solid cylindrical portion 21a and the hollow cylindrical portion 22a are partitioned by a partition wall W. In addition, illustration of the partition W is abbreviate | omitted in FIG.2 (b).

  As shown in FIG. 2 (b), the housing 2b has openings H1, H2, H3, H4, and H5, and an opening outside the figure (hereinafter referred to as an “outside figure opening”). Yes. The opening H1 is formed in the surface on the engine 5 side of the housing 2b (the left surface in FIG. 2B). The opening H2 is formed on the surface of the housing 2b opposite to the engine 5 (the right surface in FIG. 2B). The openings H3 and H4 are formed on the upper surface of the housing 2b (the upper surface in FIG. 2B). The opening H5 is formed on the lower surface of the housing 2b (the lower surface in FIG. 2B). These openings H1, H2, H3, H4, and H5 are holes through which cooling water passes.

  In order to show the positional relationship between the openings H1, H2, H3, H4, H5 and the cutout holes K11, K12, K21, K31, K32, K33, K41, K51, FIG. H2, H3, H4, and H5 are indicated by two-dot chain lines. As shown in FIG. 2A, the openings H1, H2, H3, H4, and H5 are arranged in this order from one end side in the axial direction to the other end side of the housing 2b. As shown in FIG. 2A, the center of the opening H1 is always at the reference position 0 °.

  Between the opening H1 and the rotary valve 2a, a cylindrical lip 2c extending from the inner peripheral edge of the opening H1 toward the rotary valve 2a is provided. The end of the lip 2c on the opening H1 side is fixed to the inner periphery of the opening H1. The lip 2c is separate from the rotary valve 2a and is not fixed to the rotary valve 2a. The end surface of the lip portion 2c on the rotary valve 2a side has a shape along the outer peripheral surface of the rotary valve 2a. As a result, the end surface of the lip portion 2c on the rotary valve 2a side can be brought into sliding contact with the outer peripheral surface of the rotary valve 2a.

  A lip portion 2d similar to the lip portion 2c is also provided between the opening H2 and the rotary valve 2a, and a lip portion 2e similar to the lip portion 2c is also provided between the opening H3 and the rotary valve 2a. A lip 2f similar to the lip 2c is provided between the opening H4 and the rotary valve 2a, and a lip 2g similar to the lip 2c is provided between the opening H5 and the rotary valve 2a. Yes.

  As shown in FIG. 2A, the solid cylindrical portion 21a of the rotary valve 2a is formed with notches K11, K12, K21, K31, K32, K33 and tunnel portions T1, T2, T3. Yes.

  Cutout holes K41 and K51 are formed in the peripheral wall of the hollow cylindrical portion 22a of the rotary valve 2a. In addition, an opening 36 (see FIG. 2B) is formed at the axial end of the hollow cylindrical portion 22a (the lower end in FIG. 2A).

  The cutout holes K11, K12, K21, K31, K32, and K33 are concave portions formed at a predetermined depth from the peripheral surface of the solid cylindrical portion 21a. The depths of the cutout holes K11, K12, K21, K31, K32, and K33 are such that they do not reach the radial center of the solid cylindrical portion 21a.

  The cutout holes K41 and K51 are through holes formed in the peripheral wall of the hollow cylindrical portion 22a.

  As shown in FIG. 2A, the cutout holes K11 and K12 are arranged in the circumferential direction of the rotary valve 2a. The cutout holes K31, K32, K33 are arranged in the circumferential direction of the rotary valve 2a. The first row of cutout holes constituted by the cutout holes K11, K12, the second row of cutout holes constituted by the cutout holes K21, the third row of cutout holes constituted by the cutout holes K31, K32, K33, and the cutout holes. The fourth row of cutout holes formed of K41 and the fifth row of cutout holes formed of the cutout holes K51 are arranged in this order from one axial end to the other end of the rotary valve 2a.

  As the rotary valve 2a rotates, the positions of the cutout holes K1, K2, K3, H4, and H5 change in the circumferential direction (the left-right direction in FIG. 2A).

  The opening shape of the cutout hole K11 is a rectangular shape extending in the circumferential direction of the rotary valve 2a, and at a certain point shown in FIG. 2A (when the flow of cooling water is stopped in the entire cooling device 1). , Extending from around 30 ° to around 280 °.

  The opening shape of the cutout hole K12 has a rectangular shape extending in the circumferential direction of the rotary valve 2a, and extends from around 290 ° to around 25 ° at a certain point shown in FIG. Yes.

  The opening shape of the cutout hole K21 is a rectangular shape extending in the circumferential direction of the rotary valve 2a, and extends from around 335 ° to around 105 ° at a certain point shown in FIG. Yes.

  The opening shape of the cutout hole K31 is a rectangular shape extending in the circumferential direction of the rotary valve 2a, and extends from around 25 ° to around 110 ° at a certain point shown in FIG. Yes.

  The opening shape of the cutout hole K32 is a rectangular shape extending in the circumferential direction of the rotary valve 2a, and extends from about 120 ° to about 235 ° at a certain point shown in FIG. Yes.

  The opening shape of the cutout hole K33 is a rectangular shape extending in the circumferential direction of the rotary valve 2a, and extends from about 245 ° to about 10 ° at a certain point shown in FIG. Yes.

  The opening widths (lengths along the axial direction of the rotary valve 2a) of the cutout holes K11, K12, K21, K31, K32, and K33 are the same.

  The cutout hole K41 extends in the circumferential direction of the rotary valve 2a and has a rectangular main portion K41c whose one end in the longitudinal direction (left end portion in FIG. 2A) is recessed in a concave shape, and the other longitudinal end of the main portion K41c. A constricted portion K41b that is provided continuously to the portion (the right end portion in FIG. 2A) and constricts in a triangular shape, and a protrusion K41a that projects from the tip of the constricted portion K41b. At a certain time shown in FIG. 2A, the cutout hole K41 extends from around 200 ° to around 55 °. The width of the main portion K41c of the cutout hole K41 is larger than the opening width of the cutout holes K11, K12, K21, K31, K32, and K33.

  The cutout hole K51 extends in the circumferential direction of the rotary valve 2a and is provided continuously with a rectangular main portion K51c whose one end in the longitudinal direction is recessed in a concave shape and the other end in the longitudinal direction of the main portion K51c, and is constricted in a triangular shape. It has a rounded portion K51b and a projection K51a protruding from the tip of the narrowed portion K51b. The circumferential length of the main portion K51c is shorter than the circumferential length of the main portion K41c in the cutout hole K41, and at a certain time point shown in FIG. 2 (a), from around 355 ° to around 145 °. It extends over. The width of the main portion K51c of the cutout hole K51 is equal to the width of the main portion K41c of the cutout hole K41.

  As shown in FIG. 2A, the tunnel portion T1 (shown by a broken line) is formed inside the solid cylindrical portion 21a so as to connect the notch hole K21 and the notch hole K33. One end portion of the tunnel portion T1 opens at the inner wall surface of the notch hole K21, and the other end portion of the tunnel portion T1 opens at the inner wall surface of the notch hole K33. The cutout hole K21 and the cutout hole K33 communicate with each other through the tunnel portion T1.

  The tunnel portion T2 is formed inside the solid cylindrical portion 21a so as to connect the notch hole K12 and the notch hole K31. One end portion of the tunnel portion T2 opens at the inner wall surface of the notch hole K12, and the other end portion of the tunnel portion T2 opens at the inner wall surface of the notch hole K31. The cutout hole K12 and the cutout hole K31 communicate with each other through the tunnel portion T2. In FIG. 2A, the tunnel portion T2 and the cutout hole K21 intersect with each other, but they do not communicate with each other. The tunnel portion T2 is formed so as to bypass the notch hole K21 inside the solid cylindrical portion 21a.

  The tunnel portion T3 is formed inside the solid cylindrical portion 21a so as to connect the cutout hole K11, the cutout hole K32, and the hollow cylindrical portion 22a. One end portion of the tunnel portion T3 opens at the inner wall surface of the notch hole K11, the central portion in the length direction of the tunnel portion T3 opens at the inner wall surface of the notch hole K32, and the other end portion of the tunnel portion T3 penetrates the partition wall W. The partition wall W is opened on the surface on the hollow cylindrical portion 22a side. The cutout hole K11, the cutout hole K32, and the hollow cylindrical portion 22a communicate with each other through the tunnel portion T3.

  The opening H1 is provided at a position where the opening H1 can overlap with the cutout holes K11 and K12 according to the rotation of the rotary valve 2a, and is provided at a position centered on 0 ° shown in FIG. Yes. The diameter of the opening H1 is slightly larger than the width of the cutout holes K11 and K12. The opening H1 is connected to the end of the exhaust valve 22 on the rotary valve device 2 side.

  The opening H2 is provided at a position where the opening H2 can overlap with the cutout hole K21 in accordance with the rotation of the rotary valve 2a, and is provided at a position centered on 180 ° shown in FIG. The diameter of the opening H2 is slightly larger than the width of the cutout hole K21. The opening H2 is connected to an upstream end of a communication channel 27 (see FIG. 1) described later.

  The opening H3 is provided at a position where the opening H3 can overlap with the cutout holes K31, K32, K33 according to the rotation of the rotary valve 2a, and is provided at a position centering on 90 ° shown in FIG. It has been. The diameter of the opening H3 is slightly larger than the width of the cutout holes K31, K32, K33. The opening H3 is connected to the downstream end of the communication channel 26 (see FIG. 1).

  The opening H4 is provided at a position where the opening H4 can overlap with the notch hole K41 according to the rotation of the rotary valve 2a, and is provided at a position centering on 90 ° shown in FIG. The diameter of the opening H4 is slightly larger than the width of the cutout hole K41. The opening H4 is connected to an upstream flow path 34 in an auxiliary machine side flow path 35 (see FIG. 1) described later.

  The opening H5 is provided at a position where the opening H5 can overlap with the cutout hole K51 in accordance with the rotation of the rotary valve 2a, and is provided at a position around 270 ° shown in FIG. The diameter of the opening H5 is slightly larger than the width of the cutout hole K51. The opening H5 is connected to an upstream end of a later-described radiator-side flow path 33 (see FIG. 1).

  A gap is provided between the opening 36 (see FIG. 2B) at the axial end of the rotary valve 2a and the inner wall surface of the housing 2b facing the opening 36. The above-mentioned non-illustrated opening formed in the housing 2b is always in communication with the inside of the hollow cylindrical portion 22a of the rotary valve 2a through this gap and the cutout holes K41 and K51. The part that is always in communication is shown as a communication part 37 in FIG.

  In the rotary valve device 2, as shown in FIGS. 2 and 7, when the notch hole K12 and the opening H1 overlap and the notch hole K31 and the opening H3 overlap, FIG. 6, the exhaust side flow path 22 and the communication flow path 26 communicate with each other. That is, the communication flow path 42 that connects the exhaust side flow path 22 and the communication flow path 26 is formed in the rotary valve device 2.

  Further, as shown in FIG. 5, when the cutout hole K11 and the opening H1 overlap and the cutout hole K32 and the opening H3 overlap, as shown in FIG. The communication channel 26 and the main channel 23 communicate with each other. That is, the communication flow path 43 that connects the exhaust flow path 22, the communication flow path 26, and the main flow path 23 is formed in the rotary valve device 2.

  Further, as shown in FIG. 7, when the cutout hole K41 and the opening H4 overlap each other, as shown in FIG. 6, the main flow path 23 and the auxiliary machine side flow path 35 communicate with each other. That is, the communication flow path 44 that connects the main flow path 23 and the auxiliary machine side flow path 35 is formed in the rotary valve device 2.

  Further, as shown in FIG. 9, when the notch hole K11 and the opening H1 overlap and the notch hole K41 and the opening H4 overlap, as shown in FIG. And the main flow path 23 and the auxiliary machine side flow path 35 communicate with each other. That is, in the rotary valve device 2, a communication channel 45 that connects the exhaust-side channel 22 and the communication channel 44 and a communication channel 44 are formed.

  As shown in FIGS. 9 and 11, when the notch hole K21 and the opening H2 overlap and the notch hole K33 and the opening H3 overlap, as shown in FIGS. The flow path 26 and the communication flow path 27 communicate with each other. That is, the communication flow path 46 that connects the communication flow path 26 and the communication flow path 27 is formed in the rotary valve device 2.

  As shown in FIG. 11, when the cutout hole K11 and the opening H1 overlap, the cutout hole K41 and the opening H4 overlap, and the cutout hole K51 and the opening H5 overlap, As shown in FIG. 10, the exhaust side flow path 22, the main flow path 23, the auxiliary machine side flow path 35, and the radiator side flow path 33 communicate with each other. That is, in the rotary valve device 2, the communication channel 47, the communication channel 44, and the communication channel 45 that connect the radiator side channel 33 and the communication channel 44 are formed.

  Further, as shown in FIG. 13, the cutout hole K11 and the opening H1 overlap, the cutout hole K32 and the opening H3 overlap, the cutout hole K41 and the opening H4 overlap, and the cutout When the hole K51 and the opening H5 overlap with each other, as shown in FIG. 12, the exhaust side flow path 22, the main flow path 23, the communication flow path 26, the auxiliary machine side flow path 35, and the radiator side flow path 33 Communicate. That is, in the rotary valve device 2, a communication channel 48 that connects the communication channel 26 and the communication channel 44, a communication channel 44, a communication channel 45, and a communication channel 47 are formed.

  In the rotary valve device 2, the area where the cutout hole K11 and the opening H1 overlap and the area where the cutout hole K12 and the opening H1 overlap change according to the rotation of the rotary valve 2a. That is, the flow rate regulating valve is configured by the cutout holes K11 and K12 and the opening H1. In the following description, the flow rate control valve configured by the cutout holes K11 and K12 and the opening H1 is referred to as a flow rate control valve V1 (see FIG. 1).

  Similarly, a flow rate adjusting valve is configured by the cutout hole K21 and the opening H2. Further, the flow rate regulating valve is constituted by the cutout holes K31, K32, K33 and the opening H3. Further, the flow rate adjusting valve is constituted by the cutout hole K41 and the opening H4. Further, the flow rate adjusting valve is configured by the cutout hole K51 and the opening H5.

  In the following description, the flow control valve configured by the cutout hole K21 and the opening H2 is referred to as a flow control valve V2 (see FIG. 1), and the flow control valve configured by the cutout holes K31, K32, K33 and the opening H3. Is referred to as a flow rate adjusting valve V3, a flow rate adjusting valve constituted by the notch hole K41 and the opening H4 is referred to as a flow rate adjusting valve V4, and a flow rate adjusting valve constituted by the notch hole K51 and the opening H5 is referred to as a flow rate adjusting valve V5. Called.

  As shown in FIGS. 3 and 6, when the flow control valve V1 and the flow control valve V3 communicate with each other, the cooling water can flow between the exhaust side flow path 22 and the communication flow path 26. become. As shown in FIG. 4, when the flow rate control valve V <b> 1, the flow rate control valve V <b> 3, and the communication portion 37 are in communication, the exhaust side flow path 22, the communication flow path 26, and the main flow path 23 are connected. Cooling water can flow between them. In addition, as shown in FIG. 6, when the communication part 37 and the flow rate control valve V4 are in communication, the cooling water can flow between the main flow path 23 and the auxiliary machine side flow path 35. become.

  Further, as shown in FIG. 8, when the flow rate control valve V1, the communication portion 37, and the flow rate control valve V4 are in communication, the exhaust side flow path 22, the main flow path 23, and the auxiliary machine side flow path 35. Cooling water can flow between them. As shown in FIGS. 8 and 10, when the flow rate control valve V <b> 2 and the flow rate control valve V <b> 3 are in communication, the cooling water may flow between the communication channel 26 and the communication channel 27. It becomes possible.

  Further, as shown in FIG. 10, when the flow rate control valve V1, the communication portion 37, the flow rate control valve V4, and the flow rate control valve V5 are in communication, the exhaust side flow path 22, the main flow path 23, and the auxiliary flow path are supplemented. Cooling water can flow between the machine side flow path 35 and the radiator side flow path 33. In addition, as shown in FIG. 12, when the flow control valve V1, the communication portion 37, the flow control valve V3, the flow control valve V4, and the flow control valve V5 are in communication, the exhaust side flow path 22 and the main Cooling water can flow between the flow path 23, the communication flow path 26, the accessory-side flow path 35, and the radiator-side flow path 33.

  That is, the flow rate control valves V1, V2, V3, V4, and V5 constitute a flow path switching valve that switches the flow path of the cooling water.

  In order to circulate the cooling water in the heater circulation path 40, (i) when the heater-side pump 4 is in operation, as shown in FIGS. As shown in FIGS. 8 and 10, when the control valve V3 is in communication, or (ii) at least the auxiliary pump 3 of the auxiliary pump 3 and the heater pump 4 is operating, It is necessary to connect the control valve V1 and the flow rate control valve V4, and to connect the flow rate control valve V2 and the flow rate control valve V3. The reason will be described later.

<Configuration of circulation path 41 for auxiliary machinery>
The auxiliary circuit circulation path 41 (see FIG. 1) is a path through which the cooling water circulates. The block side flow path 25, the main flow path 23, the flow path in the rotary valve device 2, the upstream flow path 34, and the oil cooler. A side channel 20, an EGR valve side channel 21, an EGR cooler side channel 17, a return channel 16, and a radiator side channel 33 are provided. The auxiliary machine circulation path 41 corresponds to the “second circulation path” in the present invention.

  The oil cooler side flow path 20, the EGR valve side flow path 21, the EGR cooler side flow path 17, and the return flow path 16 constitute an auxiliary machine side flow path 35.

  The block-side flow path 25 is a flow path that passes through the cylinder block 5B. The upstream end of the block side flow path 25 is connected to the discharge port of the auxiliary machine side pump 3.

  The main flow path 23 is a flow path that passes through a portion other than the exhaust port side portion of the cylinder head 5A, that is, a portion around the combustion chamber and a portion on the intake port side. The end of the main channel 23 opposite to the rotary valve device 2 is connected to the block-side channel 25.

  The upstream side flow path 34 supplies the cooling water flowing out from the opening H4 (flow rate control valve V4) of the rotary valve device 2 to the oil cooler side flow path 20, the EGR valve side flow path 21, and the EGR cooler side flow path 17. It is a flow path for guiding. The upstream end of the upstream channel 34 is connected to the opening H4. The downstream end of the upstream channel 34 is connected to the upstream ends of the oil cooler channel 20, the EGR valve channel 21, and the EGR cooler channel 17. The upstream flow path 34 is provided with a water temperature sensor 8 that detects the temperature of the cooling water.

  The downstream end of the oil cooler side flow path 20 is connected to the return flow path 16. An oil cooler 10 is provided in the oil cooler side flow path 20.

  The downstream end of the EGR valve side channel 21 is connected to the return channel 16. An EGR valve 11 and an ATF warmer 12 are provided in the EGR valve side flow path 21.

  The upstream end of the radiator-side flow path 33 is connected to the opening H5 (flow rate adjustment valve V5) of the rotary valve device 2. The downstream end of the radiator side flow path 33 is connected to the return flow path 16. The radiator 14 is provided in the radiator-side flow path 33.

  The return flow path 16 is a flow path for returning the cooling water flowing out from the oil cooler side flow path 20, the EGR valve side flow path 21, the radiator side flow path 33, and the EGR cooler side flow path 20 to the auxiliary machine side pump 3. It is. The oil cooler side flow path 20, the EGR valve side flow path 21, the radiator side flow path 33, and the downstream end portions of the EGR cooler side flow path 20 are connected to the upstream portion or the midstream portion of the return flow passage 16. The downstream end of the return flow path 16 is connected to the suction port of the auxiliary machine side pump 3.

  In order to circulate the cooling water in the auxiliary machine circulation path 41, the communication portion 37 and the flow rate control valve V4 need to be in communication with each other while the auxiliary pump 3 is operating (FIG. 6, FIG. 6). 8, 10, 12).

<Configuration of communication channel 27>
The communication flow path 27 is a flow path that connects the middle portion of the return flow path 16 and the flow rate control valve V2. The upstream end portion of the communication flow path 27 is connected to the flow rate control valve V <b> 2, and the downstream end portion of the communication flow path 27 is connected to the middle portion of the return flow path 16. In the example shown in FIG. 1, the downstream end portion of the communication flow path 27 is connected to a portion of the return flow path 16 upstream of the connection point between the return flow path 16 and the EGR cooler-side flow path 17. The communication channel 27 corresponds to the “first communication channel” in the present invention.

<Configuration of water temperature sensor and various sensors>
The water temperature sensor 24 is provided in the main channel 23 and detects the temperature of the cooling water flowing through the main channel 23. The water temperature sensor 7 is provided downstream of the heater core 6 in the heater side flow path 15 and detects the temperature of the cooling water flowing out of the heater core 6. The water temperature sensor 8 is provided in the upstream flow path 34 and detects the temperature of the cooling water flowing out from the rotary valve device 2. The accelerator opening sensor 30 detects the amount of depression of the accelerator pedal by the driver as the accelerator opening. The crank angle sensor 32 detects the rotation angle of the crankshaft. The intake air temperature sensor 38 detects the temperature of intake air flowing into the engine 5.

  The water temperature sensor 8, the accelerator opening sensor 30, the crank angle sensor 32, and the intake air temperature sensor 38 correspond to “temperature detection means” of the present invention.

<Configuration of ECU 31>
The ECU 31 includes a CPU, RAM, ROM, and the like. The ECU 31 generates a control signal for controlling the operations of the rotary valve device 2 and the heater-side pump 4 based on signals indicating detection values received from the water temperature sensor 24, the accelerator opening sensor 30, and the crank angle sensor 32. Then, the control signal is transmitted to the rotary valve device 2 and the heater side pump 4. The ECU 31 corresponds to a “temperature detection unit” and a “control unit” of the present invention.

  The detected values of the water temperature sensors 7 and 8 are used to determine whether the heater core 6 and the engine 5 are appropriately temperature-controlled while the ECU 31 controls the rotary valve device 2 and the heater-side pump 4. It is done. In the following description, the description of the control operation of the rotary valve device 2 and the heater side pump 4 using the detection values of the water temperature sensors 7 and 8 is omitted.

  Next, the control operation of the rotary valve device 2 and the heater side pump 4 by the ECU 31 will be described with reference to the flowcharts of FIGS. It is assumed that the engine 5 has already been started and the auxiliary pump 3 is operating with the power of the engine 5.

  As shown in FIG. 14, first, the ECU 31 inputs signals indicating detection values from the water temperature sensor 24, the accelerator opening sensor 30, the crank angle sensor 32, and the intake air temperature sensor 38 (step S1).

  Next, the ECU 31 calculates an engine load generated by the engine (a driving torque generated by the engine) based on the accelerator opening detected by the accelerator opening sensor 30 (step S2).

  Next, the ECU 31 calculates the engine speed based on the crank angle detected by the crank angle sensor 32 (step S3).

  Next, the ECU 31 determines the wall surface temperature of the combustion chamber on the cylinder head 5A side of the engine 5 (hereinafter referred to as “combustion chamber wall temperature”) based on the coolant temperature, engine load, engine speed, and intake air temperature. Calculate (step S4). This combustion chamber wall temperature corresponds to the “engine temperature” in the present invention.

  Next, the ECU 31 determines whether or not the combustion chamber wall temperature is in a temperature range of level 0 (step S5). The temperature range of level 0 is a temperature lower than the temperature T0 corresponding to the cold state, and is included in the “first temperature range” in the present invention.

  When the ECU 31 makes a determination of YES in step S5, as shown in FIG. 1, the ECU 31 performs a control for setting the flow rate control valve V1 and the flow rate control valve V3 to be in communication with each other and stopping the heater-side pump 4. It performs (step S6).

  By performing the control in step S6, as shown in FIG. 2A, in the rotary valve device 2, the opening H1 and the notch hole K12 overlap, and the opening H2 and the notch hole K21 do not overlap. The opening H3 and the cutout hole K31 overlap, the opening H4 and the cutout hole K41 do not overlap, and the opening H5 and the cutout hole K51 do not overlap. As a result, as shown in FIG. 1, a communication flow path 42 that connects the exhaust side flow path 22 and the communication flow path 26 is formed in the rotary valve device 2, but the heater side pump 4 is stopped. Therefore, the cooling water does not circulate in the heater circulation path 40. Further, since the communication flow path connecting the main flow path 23 and the auxiliary machine side flow path 35 is not formed in the rotary valve device 2, the cooling water does not circulate also in the auxiliary machine circulation path 41. Thus, since cooling water does not flow in any flow path of the cooling device 1, warming up of the engine 5 is promoted. Hereinafter, the control state of step S6 is referred to as a “water stop state”. After executing the process of step S6, the ECU 31 returns to step S1.

  When it is determined NO in step S5, the ECU 31 determines whether the combustion chamber wall temperature is in the level 1 temperature range (step S7). The temperature range of level 1 is a temperature range (during warming-up) that is equal to or higher than temperature T0 and lower than T1, and is included in the “first temperature range” in the present invention.

  When the ECU 31 makes a determination of YES in step S7, the flow control valve V1 and the flow control valve V3 are in communication with each other as shown in FIG. Step S8). The heater-side pump 4 operates in such a direction that the cooling water flows from the heater-side channel 15 side to the connecting channel 26 and the ETB-side channel 19 side. The same applies to other steps in which the heater side pump 4 operates.

  By performing the control in step S8, as shown in FIG. 3, the cooling water is supplied to the exhaust side flow path 22, the heater side flow path 15, the communication flow path 26, the communication flow path 42, and the ETB side flow path 19. Flowing. That is, the cooling water circulates in the heater circulation path 40 including the exhaust side flow path 22, the heater side flow path 15, the communication flow path 26, the communication flow path 42, and the ETB side flow path 19. Hereinafter, the control state in step S8 is referred to as “control state A”. The ECU 31 returns to step S1 after executing the process of step S8.

  When it is determined NO in step S7, the ECU 31 determines whether the combustion chamber wall temperature is in the temperature range of level 2 (step S9). The temperature range of level 2 is a temperature range that is equal to or higher than temperature T1 and lower than T2 (during warm-up), and is included in the “first temperature range” in the present invention.

  If the ECU 31 makes a determination of YES in step S9, the flow control valve V1, the communication portion 37, and the flow control valve V3 are in communication with each other as shown in FIG. Control is performed (step S10).

  Specifically, when the rotary valve 2a rotates in the housing 2b, as shown in FIG. 5, in the rotary valve device 2, the opening H1 and the cutout hole K11 overlap each other, and the opening H2 and the cutout hole K21 are overlapped. Does not overlap, the opening H3 and the cutout hole K32 overlap, the opening H4 and the cutout hole K41 do not overlap, and the opening H5 and the cutout hole K51 do not overlap. As a result, as shown in FIG. 4, a communication flow path 43 that connects the exhaust-side flow path 22, the main flow path 23, and the communication flow path 26 is formed in the rotary valve device 2.

  And the part on the opposite side to the rotary valve apparatus 2 in the exhaust side flow path 22, the main flow path 23, and the block side flow path 25, the heater side flow path 15, the communication flow path 26, the communication flow path 43, and the ETB side flow The path 19 constitutes a heater circulation path 40. The cooling water circulates in the heater circulation path 40 by the pumping force of the heater-side pump 4. Hereinafter, the control state of step S10 is referred to as “control state B”. The ECU 31 returns to step S1 after executing the process of step S10.

  If the determination in step S9 is NO, the ECU 31 determines whether or not the combustion chamber wall temperature is in the temperature range of level 3 (step S11). The temperature range of level 3 is a temperature range (during warm-up) that is equal to or higher than temperature T2 and lower than T3, and is included in the “first temperature range” in the present invention.

  When the ECU 31 makes a determination of YES in step S11, as shown in FIG. 6, the flow control valve V1 and the flow control valve V3 communicate with each other, and the communication unit 37 and the flow control valve V4 communicate with each other. The flow control valve V4 is set to a small opening, and the heater side pump 4 is controlled to operate (step S12).

  Specifically, as shown in FIG. 7, the ECU 31 moves the rotary valve 2a so that the cutout holes K11, K12, K21, K31, K32, K33, K41, K51 advance from the left side to the right side in FIG. Rotate (hereinafter referred to as “right rotation”). By rotating the rotary valve 2a, as shown in FIG. 7, in the rotary valve device 2, the opening H1 and the cutout hole K12 overlap (the flow rate control valve V1 is fully open), and the opening H2 and the cutout hole K21. And the opening H3 and the cutout hole K31 overlap (the flow control valve V3 is fully open), the opening H4, the protrusion K41a of the cutout hole K41, and the constriction. The gap portion K41b overlaps (the flow rate adjustment valve V4 is in a small opening state), and the opening portion H5 and the cutout hole K51 do not overlap (the flow rate adjustment valve V5 is in a fully closed state).

  Thereby, as shown in FIG. 6, a communication flow path 42 that connects the exhaust side flow path 22 and the communication flow path 26 is formed in the rotary valve device 2, and the main flow path 23 and the auxiliary machine side flow path 35 are formed. Is formed. The communication channel 42 and the communication channel 44 are independent of each other.

  The exhaust side flow path 22, the heater side flow path 15, the communication flow path 26, the communication flow path 42, and the ETB side flow path 19 constitute a heater circulation path 40. The cooling water circulates in the heater circulation path 40 by the pumping force of the heater-side pump 4.

  Further, an auxiliary machine circulation path 41 is constituted by the block side flow path 25, the main flow path 23, the communication flow path 44, and the auxiliary machine side flow path 35. The cooling water circulates in this auxiliary machine circulation path 41 by the pumping force of the auxiliary machine side pump 3.

  Since the communication flow path 42 and the communication flow path 44 are independent from each other, the cooling water does not flow through the flow path between the heater circulation path 40 and the auxiliary machine circulation path 41. That is, the heater circulation path 40 and the auxiliary machine circulation path 41 are independent circulation paths in which the cooling water is not mixed, and the cooling water circulates separately in each circulation path.

  Further, since the flow rate adjusting valve V4 is in a small opening state, when the flow rate adjusting valve V4 is opened, the auxiliary side channel 35, that is, the oil cooler side channel 20, the EGR valve side channel 21, EGR is opened. It is possible to prevent a large amount of low-temperature cooling water in the cooler-side channel 17 and the return channel 16 from flowing into the main channel 23 in a short time.

  In step S12, the opening H4 starts to overlap from the protrusion K41a of the cutout hole K41 (see FIG. 7). Therefore, the flow rate is limited to a small amount during the initial predetermined period in which the main flow path 23 and the auxiliary machine side flow path 35 are connected. Thereafter, the flow rate gradually increases until the opening H4 overlaps the protrusion K41a and the narrowed portion K41b of the cutout hole K41. Therefore, when the main flow path 23 and the auxiliary machine side flow path 35 are connected, the low-temperature cooling water in the auxiliary machine side flow path 35 gradually flows into the main flow path 23, so that the rapid temperature around the combustion chamber is increased. The decrease can be suppressed. Hereinafter, the control state of step S12 is referred to as “control state C”.

  If NO is determined in step S11, the ECU 31 determines whether or not the combustion chamber wall temperature is in the temperature range of level 4 as shown in FIG. 15 (step S13). The temperature range of level 4 is a temperature range (during warm-up) that is equal to or higher than temperature T3 and lower than T4, and is included in the “second temperature range” in the present invention. The temperature T4 is a temperature that serves as a criterion for determining whether or not the engine is warming up. That is, if the combustion chamber wall temperature is lower than T4, the engine is warming up, and if it is equal to or higher than T4, the engine is in a warming-up completed state.

  If the ECU 31 makes a determination of YES in step S13, as shown in FIG. 8, in the rotary valve device 2, the flow control valve V1, the communication portion 37, and the flow control valve V4 are in communication with each other. The control valve V2 and the flow rate control valve V3 are communicated, the flow rate control valve V4 is set to a large opening (a state where the opening is slightly smaller than the fully opened state), and the heater side pump 4 is controlled to stop ( Step S14).

  Specifically, the ECU 31 rotates the rotary valve 2a to the right (see FIG. 9). When the rotary valve 2a rotates to the right, as shown in FIG. 9, in the rotary valve device 2, the opening H1 and the cutout hole K11 overlap (the flow control valve V1 is in a large opening state), and the opening H2 and the cutout The hole K21 overlaps (the flow control valve V2 is in a large opening state), the opening H3 and the cutout hole K33 overlap (the flow control valve V3 is in a large opening state), and the opening H4 and the constriction K41b of the cutout hole K41. In addition, the main portion K41c overlaps (the flow control valve V4 is in a large opening state), and the opening H5 and the cutout hole K51 do not overlap (the flow control valve V3 is in a fully closed state).

  As the opening degree of the flow rate adjustment valve V4 increases, the amount of cooling water flowing out from the rotary valve device 2 to the auxiliary machine side flow path 35 increases.

  By performing the control in step S14, as shown in FIG. 8, the communication valve 44, the communication channel 45 connecting the exhaust side channel 22 and the communication channel 44, and the communication are connected in the rotary valve device 2. A communication channel 46 that connects the channel 27 and the communication channel 26 is formed.

  The communication channel 46 corresponds to the “first communication channel” in the present invention. Opening the communication flow path 27 by forming the communication flow path 46 (the state shown in FIGS. 8 and 10) corresponds to the “opening of the first communication flow path” in the present invention. By not forming the passage 46, the communication flow path 27 is closed (the state shown in FIGS. 1, 3, 4, 6, and 12), which corresponds to the “first communication flow path closing” in the present invention. .

  The communication channel 45 corresponds to the “second communication channel” in the present invention. Then, by forming the communication flow path 45, the exhaust side flow path 22 and the communication flow path 44 are connected (as shown in FIGS. 8, 10, and 12). Corresponding to “open”, forming the communication flow path 42 or the communication flow path 43 without forming the communication flow path 45 (the state shown in FIGS. 1, 3, 4 and 6) is the “second” in the present invention. This corresponds to “closing the communication channel”.

  By performing the control in step S14, the heater-side flow path 15, the communication flow path 26, the communication flow path 46, the communication flow path 27, the return flow path 16, and the block-side flow path 25 on the opposite side to the rotary valve device 2. The heater circulation path 40 is configured by the portion, the portion of the exhaust side flow path 22 opposite to the rotary valve device 2, and the ETB side flow path 19. The cooling water is circulated in the heater circulation path 40 by the pumping force of the auxiliary machine side pump 3.

  Further, an auxiliary machine circulation path 41 is constituted by the block side flow path 25, the main flow path 23, the communication flow path 44, the exhaust side flow path 22, the communication flow path 45, and the auxiliary machine side flow path 35. The cooling water circulates in this auxiliary machine circulation path 41 by the pumping force of the auxiliary machine side pump 3.

  Here, the reason why the cooling water circulates in the heater circulation path 40 by the pumping force of the auxiliary machine side pump 3 will be described.

  In a state where the auxiliary pump 3 is driven by the power of the engine 5 (see FIG. 6), the upstream side portion of the auxiliary machines 9, 10, 11 and 12 in the auxiliary circulation path 41 is the auxiliary machine 9, The pressure of the cooling water is higher than that of the downstream portions of 10, 11, 12. For this reason, a pressure difference arises between the return flow path 16 (low pressure) and the communication flow path 44 (high pressure).

  In order to utilize this pressure difference for the circulation of the cooling water in the heater circulation path 40, as shown in FIG. 8, the communication flow path 46 is formed to open the communication flow path 27 and the exhaust side flow path 22. And a communication channel 45 that connects the communication channel 44 to each other. As a result, a pressure difference is generated by the auxiliary pump 3 between two points P1 and P2 (see FIG. 8) that are separated from each other in the heater circulation path 40. P1 is a connection point (low pressure) between the return flow path 16 and the communication flow path 27, and P2 is a connection point (high pressure) between the heater side flow path 15 and the exhaust side flow path 22. By generating a pressure difference between P1 and P2, the cooling water is circulated in the heater circulation path 40 using the pumping force of the auxiliary pump 3. Since the cooling water can be circulated in the heater circulation path 40 using the pumping force of the auxiliary pump 3, the cooling water is circulated in the heater circulation path 40 with the heater pump 4 stopped. Can be made.

  That is, by the control in step S14, a pressure difference is generated by the auxiliary pump 3 between the two points P1 and P2 that are separated from each other in the heater circulation path 40, so that the heater using the pumping force of the auxiliary pump 3 is utilized. The cooling water is circulated through the circulation path 40, and as a result, the load applied to the heater-side pump 4 can be reduced, and the power consumption and the life of the heater-side pump 4 can be reduced.

  Hereinafter, the control state of step S14 is referred to as “control state D”.

  If the ECU 31 determines NO in step S13, the ECU 31 determines whether the engine load is less than a predetermined threshold (step S15). The threshold value is a value that serves as a criterion for determining whether or not the engine 5 is in a high load state. That is, if the engine load is less than the threshold value, the engine 5 is in a low load or medium load state, and if the engine load is equal to or greater than the threshold value, the engine 5 is in a high load state. If NO is determined in step S13, the combustion chamber wall temperature is T4 or higher. The temperature range of T4 or higher corresponds to the “third temperature range” in the present invention.

  When the ECU 31 makes a determination of YES in step S15, as shown in FIG. 10, in the rotary valve device 2, the flow rate control valve V1, the communication unit 37, the flow rate control valve V4, and the flow rate control valve V5 communicate with each other. The flow rate control valve V2 and the flow rate control valve V3 are in communication, the flow rate control valve V4 is fully open, the flow rate control valve V5 is open, and the heater side pump 4 Control to stop is performed (step S16).

  Specifically, the ECU 31 rotates the rotary valve 2a to the right (see FIG. 11). When the rotary valve 2a rotates to the right, as shown in FIG. 11, in the rotary valve device 2, the opening H1 and the cutout hole K11 overlap (the flow control valve V1 is fully open), and the opening H2 and the cutout hole K21 overlaps (flow rate control valve V2 is fully open), opening H3 and notch hole K33 overlap (flow rate control valve V3 is fully open), and opening H4 overlaps main portion K41c of notch hole K41 ( The flow rate control valve V4 is fully open), and the opening H5 and the protrusion K51a, the narrowed portion K51b, and the main portion K51c of the cutout hole K51 overlap each other (the flow rate control valve V5 is in the middle opening state).

  As the opening degree of the flow rate adjustment valve V4 increases, the amount of cooling water flowing out from the rotary valve device 2 to the auxiliary machine side flow path 35 increases.

  By performing the control of step S16, as shown in FIG. 10, in the rotary valve device 2, the communication flow path 44, the communication flow path 45 connecting the exhaust side flow path 22 and the communication flow path 44, and the radiator A communication channel 47 that connects the side channel 33 and the communication channel 44 and a communication channel 46 that connects the communication channel 27 and the communication channel 26 are formed.

  The heater-side flow path 15, the communication flow path 26, the communication flow path 46, the communication flow path 27, the return flow path 16, the portion on the opposite side of the block-side flow path 25 from the rotary valve device 2, the exhaust-side flow path 22. The heater circulation path 40 is configured by the portion on the opposite side to the rotary valve device 2 and the ETB side flow path 19. The cooling water is circulated in the heater circulation path 40 by the pumping force of the auxiliary machine side pump 3.

  Further, the block side flow path 25, the main flow path 23, the communication flow path 44, the exhaust side flow path 22, the communication flow path 45, the auxiliary machine side flow path 35, the communication flow path 47, and the radiator side flow path 33 are used for auxiliary equipment. A circulation path 41 is formed. The cooling water circulates in this auxiliary machine circulation path 41 by the pumping force of the auxiliary machine side pump 3.

  Further, since the flow rate control valve V5 is in the middle opening state, it is possible to prevent a large amount of low-temperature cooling water in the radiator-side flow path 33 from flowing into the main flow path 23 in a short time.

  Further, in step S16, as shown in FIG. 11, the opening H5 starts to overlap from the protrusion K51a of the cutout hole K51. Accordingly, the flow rate is limited to a small amount during the initial predetermined period when the main flow path 23 and the radiator side flow path 33 are connected. Thereafter, the flow rate gradually increases until the opening H5 overlaps the protrusion K51a and the narrowed portion K51b of the cutout hole K51. Accordingly, when the main flow path 23 and the radiator side flow path 33 are connected, the low-temperature cooling water in the radiator side flow path 33 gradually flows into the main flow path 23, so that a rapid temperature drop around the combustion chamber is prevented. Can be suppressed. Hereinafter, the control state of step S16 is referred to as “control state E”.

  When the ECU 31 makes a NO determination in step S15, as shown in FIG. 12, in the rotary valve device 2, the flow control valve V1, the communication unit 37, the flow control valve V3, the flow control valve V4, and the flow control are performed. Control is performed to operate the heater-side pump 4 with the valve V5 in communication, the flow control valve V4 with a medium opening, and the flow control valve V5 with a large opening (step S17). .

  Specifically, the ECU 31 rotates the rotary valve 2a to the right (see FIG. 13). When the rotary valve 2a rotates to the right, as shown in FIG. 13, in the rotary valve device 2, the opening H1 and the cutout hole K11 overlap (the flow control valve V1 is fully open), and the opening H2 and the cutout hole K21 does not overlap (flow control valve V2 is fully closed), opening H3 and notch hole K32 overlap (flow control valve V3 is fully open), opening H4 and main portion K41c of notch hole K41. One end portion (recess side) overlaps (flow rate adjusting valve V4 is in a medium opening state), and opening portion H5 and one end portion (recess side) of main portion K51c of notch hole K51 greatly overlap (flow rate control valve V5). Is a large opening state).

  Since the opening degree of the flow rate adjusting valve V5 becomes larger than the opening degree of the flow rate adjusting valve V4, the amount of cooling water flowing out from the rotary valve device 2 to the auxiliary machine side flow path 35 is larger from the rotary valve device 2 to the radiator side. The amount of cooling water flowing out to the flow path 33 is larger.

  By performing the control in step S17, as shown in FIG. 12, in the rotary valve device 2, the communication flow path 44, the communication flow path 45 connecting the exhaust side flow path 22 and the communication flow path 44, and the radiator A communication flow path 47 that connects the side flow path 33 and the communication flow path 44 and a communication flow path 48 that connects the communication flow path 26 and the communication flow path 44 are formed.

  The heater side flow path 15, the communication flow path 26, the communication flow path 48, the auxiliary machine side flow path 35, the portion on the opposite side of the block side flow path 25 from the rotary valve device 2, the rotary valve in the exhaust side flow path 22. The heater circulation path 40 is configured by the portion on the opposite side of the apparatus 2 and the ETB side flow path 19. The cooling water circulates in the heater circulation path 40 by the pumping force of the auxiliary machine side pump 3 and the heater side pump 4.

  Further, the block side flow path 25, the main flow path 23, the communication flow path 44, the exhaust side flow path 22, the communication flow path 45, the auxiliary machine side flow path 35, the communication flow path 47, and the radiator side flow path 33 are used as auxiliary equipment. A circulation path 41 is formed. The cooling water circulates in this auxiliary machine circulation path 41 by the pumping force of the auxiliary machine side pump 3. Cooling water flows from the heater circulation path 40 into the auxiliary machine-side flow path 35 and the radiator-side flow path 33 through the communication flow path 48. Therefore, the amount of cooling water flowing through the auxiliary machine side flow path 35 and the radiator side flow path 33 is larger than that in step S16. Therefore, the cooling capacity of the cooling device 1 is improved. Hereinafter, the control state of step S17 is referred to as “control state F”.

  As described above, according to the present embodiment, in the control states A to C, the cooling water heated by the cylinder head 5A is supplied to the heater core 6 by the pumping force of the heater-side pump 4, and in the control states D and E, Since the cooling water heated by the cylinder head 5A is supplied to the heater core 6 by using the pumping force of the auxiliary pump 3, the heater circulation path 40 (first circulation path) and the auxiliary circulation path 41 ( In the cooling water circulation system in which the second circulation path) is separately provided, it is possible to reduce the load applied to the heater side pump 4 (first pump) provided in the heater circulation path 40 (first circulation path). It is possible to reduce power consumption and improve the life of the heater-side pump 4.

  That is, in the control states D and E, the pressure difference of the auxiliary pump 3 is generated between the two points P1 and P2 separated from each other in the heater circulation path 40, so that the pumping force of the auxiliary pump 3 is used. Cooling water is circulated through the heater circulation path 40. As a result, the load applied to the heater-side pump 4 can be reduced, and the power consumption and life of the heater-side pump 4 can be reduced.

  Further, in the present embodiment, since the cooling water flows through the radiator-side flow path 33 from the latter stage of warming up to the completion of the warming up, the cooling water can be cooled by the radiator 14 from the latter stage of warming up.

  In the present embodiment, in the control state F, the heater-side pump 4 is operated with the communication flow path 48 connected to the communication flow path 44. Therefore, after the warm-up is completed, the auxiliary machine-side flow path 35 and The cooling capacity of the cooling device 1 can be improved by increasing the amount of cooling water flowing through the radiator-side flow path 33. That is, in a state in which the communication flow path 27 is opened as in the control states D and E, a part of the cooling water discharged from the heater side pump 4 is downstream without passing through the auxiliary machines 9 to 12 and the radiator 14. However, when the communication flow path 27 is closed as in the control state F, most of the cooling water discharged from the heater side pump 4 is compensated. Since it flows via the machines 9 to 12 and the radiator 14, it is possible to suppress a decrease in cooling performance.

  In the present embodiment, the heater circulation path 40 includes the exhaust port side portion 5a of the cylinder head 5A, so that the heater core 6 can be warmed up. That is, since high temperature exhaust gas flows through the exhaust port, the cooling water flowing through the exhaust port side portion 5a of the cylinder head 5A is quickly warmed and warmed to a high temperature. Therefore, the heat of the exhaust port side portion 5a of the cylinder head 5A is given to the heater core 6, and the temperature rise of the heater core 6 is promoted.

  In the present embodiment, a partition wall 28 is provided between the exhaust port side portion 5a of the cylinder head 5A and the portion 5b other than the exhaust port side of the cylinder head 5A, and the exhaust port side portion 5a is interposed via the partition wall 28. And the portion 5b other than the exhaust port side are formed separately from each other. Therefore, the heat of the exhaust port side portion 5a of the cylinder head 5A can be preferentially used for raising the temperature of the heater core 6, and the heater core 6 Is further promoted.

  Further, in the present embodiment, in the control states D and E, the ECU 31 performs control to stop the heater-side pump 4, so that it is possible to promote power consumption reduction and life extension of the heater-side pump 4.

  In addition, in the said embodiment, in the control states D and E, the heater side pump 4 is stopped, but it is not restricted to this. That is, in the control states D and E, the discharge amount of the heater side pump 4 may be smaller than that in the control states A to C. That is, even if the heater side pump 4 is used in such a manner that the discharge amount of the heater side pump 4 is suppressed and the auxiliary side pump 3 is assisted, the load on the heater side pump 4 can be reduced.

  Further, in the control state F in the above embodiment, the discharge amount of the heater-side pump 4 may be controlled to be the same as the control states A to C, but so as to increase from the control states A to C. It is preferable to control. If the discharge amount of the heater-side pump 4 is controlled so as to increase more than the control states A to C, the amount of cooling water flowing through the auxiliary machines 9 to 13 and the amount of cooling water flowing through the radiator 14 increase. The cooling performance can be further improved.

  Further, in the control state F, it is more preferable to control the discharge amount of the heater side pump 4 so as to increase to the maximum discharge amount allowed for the heater side pump 4 or near the maximum discharge amount. By controlling in this way, the amount of cooling water flowing through the auxiliary machines 9 to 13 and the amount of cooling water flowing through the radiator 14 are further increased, so that the cooling performance of the cooling device 1 can be further improved.

1 Engine cooling device 2 Rotary valve device (flow path switching valve, flow control valve)
3 Auxiliary machine side pump (second pump)
4 Heater side pump (first pump)
5 Engine 5A Cylinder head 5B Cylinder block 5a Cylinder head exhaust port side part 5b Cylinder head part other than exhaust port side part 6 Heater core 9 EGR cooler 10 Oil cooler 11 EGR valve 12 ATF warmer 14 Radiator 15 Heater side flow path 16 Return Channel 17 EGR cooler side channel 19 ETB side channel 20 Oil cooler side channel 21 EGR valve side channel 22 Exhaust side channel 23 Main channel 24 Water temperature sensor (temperature detection means)
25 Block side flow path 26, 42, 43, 44, 47, 48 Communication flow path 27, 46 Communication flow path (first communication flow path)
28 Bulkhead 30 Accelerator opening sensor 31 ECU (control unit, temperature detection means)
32 Crank angle sensor 33 Radiator side flow path 34 Upstream side flow path 35 Auxiliary machine side flow path 37 Communication section 38 Intake air temperature sensor 40 Heater circulation path (first circulation path)
41 Auxiliary machinery circulation route (second circulation route)
45 Communication channel (second communication channel)
H1, H2, H3, H4, H5 Opening K11, K12, K21, K31, K32, K33, K41, K51 Notch hole V1, V2, V3, V4, V5 Flow control valve

Claims (8)

A first circulation path through which cooling water circulates through a predetermined portion in the cylinder head and the heater core of the air conditioner;
A second circulation path through which cooling water circulates through a part in the cylinder head other than the predetermined part and an auxiliary machine outside the cylinder head;
Temperature detection means for detecting the temperature of the engine;
An electric first pump that is provided in the first circulation path and pumps cooling water;
A second pump that is provided in the second circulation path, operates under the power of the engine, and pumps cooling water;
A first communication channel connecting a portion of the second circulation path on the downstream side of the auxiliary machine and the first circulation path;
A second communication flow path connecting the upstream portion of the auxiliary machine in the second circulation path and the first circulation path;
A flow path switching valve for opening and closing the first communication flow path and opening and closing the second communication flow path;
A control unit for controlling the operation of the flow path switching valve based on the detection result of the temperature detection means,
When the temperature detected by the temperature detection means during the warming up of the engine is in the first temperature range, the control unit performs control (i) to close the first and second communication flow paths, When the temperature detected by the temperature detecting means is in a second temperature range higher than the first temperature range, (ii) performing control to open the first and second communication flow paths. And an engine cooling device. The second circulation path includes an auxiliary machine-side flow path that passes through the auxiliary machine, and a radiator-side flow path that is connected in parallel to the auxiliary machine-side flow path and passes through the radiator,
The flow path switching valve further performs opening and closing of the auxiliary machine side flow path and opening and closing of the radiator side flow path,
The control unit performs control to close the radiator side flow path and open the auxiliary machine side flow path in the control of (ii), and the temperature detected by the temperature detection unit is the second temperature range. (Iii) Control to open the auxiliary machine side flow path, the radiator side flow path, the first communication flow path, and the second communication flow path when in a higher third temperature range The engine cooling device according to claim 1, wherein: The second circulation path includes an auxiliary machine-side flow path that passes through the auxiliary machine, and a radiator-side flow path that is connected in parallel to the auxiliary machine-side flow path and passes through the radiator,
The flow path switching valve further performs opening and closing of the auxiliary machine side flow path and opening and closing of the radiator side flow path,
The control unit performs control to close the radiator side flow path and open the auxiliary machine side flow path in the control of (ii), and the temperature detected by the temperature detection unit is the second temperature range. When the temperature is in the higher third temperature range, (iii) closing the first communication channel and opening the accessory side channel, the radiator side channel, and the second communication channel The engine cooling device according to claim 1, wherein control is performed.   The control unit further controls the discharge amount of the first pump based on the detection result of the temperature detection means, and in the control of (iii), the control is more than the control of (i) and (ii). The engine cooling device according to claim 3, wherein the discharge amount of the first pump is increased.   In the control of (iii), the control unit increases the discharge amount of the first pump to a maximum discharge amount allowed for the first pump or near the maximum discharge amount. The engine cooling device according to claim 4.   6. The engine cooling apparatus according to claim 1, wherein the predetermined portion in the cylinder head is an exhaust port side portion of the cylinder head.   A partition wall is provided between an exhaust port side portion of the cylinder head and a portion other than the exhaust port side of the cylinder head, and the exhaust port side portion and the portion other than the exhaust port side are mutually connected via the partition wall. The engine cooling device according to claim 6, wherein the engine cooling device is formed separately.   The control unit further controls an operating state of the first pump based on a detection result of the temperature detection unit, and stops the first pump in the control of (ii). The engine cooling device according to any one of claims 1 to 7.

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