JP6278207B2 - Engine coolant control valve device - Google Patents

Description

  The present invention relates to an engine coolant control valve device.

  Conventionally, in order to promote engine warm-up, an engine coolant control valve device for limiting circulation of coolant between the engine and a radiator during warm-up is known (see, for example, Patent Document 1). ).

  The engine coolant control valve device described in Patent Document 1 is a rotary valve device provided in a coolant flow path that connects an engine and a radiator. The rotary valve device described in Patent Document 1 includes a cylindrical rotor having an opening on the outer peripheral surface, and a housing that accommodates the rotor and has a coolant outlet that communicates with the flow path. Yes. In this rotary valve device, the rotation angle of the rotor becomes the valve opening state when the coolant outlet and the opening overlap, and the rotor rotation angle does not overlap the coolant outlet and the opening. When the angle is reached, the valve is closed.

  Furthermore, the rotary valve device described in Patent Document 1 is inserted into the coolant outlet and has a cylindrical seal member whose tip is in sliding contact with the outer peripheral surface of the rotor, and biases the seal member toward the rotor. Thus, an elastic member is provided that closely contacts the distal end portion of the seal member and the outer peripheral surface of the rotor in the valve-closed state.

  According to the coolant control device described in Patent Document 1, warm-up can be promoted by closing the rotary valve device when the coolant temperature is low, such as when the engine is started.

JP 2013-238155 A

  In the coolant control device described in Patent Literature 1, the contact pressure between the seal member and the rotor is obtained by pressing the seal member toward the rotor by the elastic member. Since the hydraulic pressure of the liquid acts (the hydraulic pressure in the direction opposite to the pressing force by the elastic member acts), the contact pressure between the seal member and the rotor is reduced by the amount of the hydraulic pressure, and the sealing member Sufficient sealing performance cannot be obtained between the rotor and the coolant may enter the coolant outlet from the rotor when the valve is closed.

  The present invention has been made in view of the above circumstances, and provides an engine coolant control valve device capable of ensuring a higher level of sealing performance and more appropriately controlling the coolant flow rate. For the purpose.

  In order to solve the above problem, the inventor of the present application sets the outer diameter of the seal member to be smaller than the inner diameter of the coolant outlet port, so that the outer peripheral surface of the seal member and the inner peripheral surface of the coolant outlet port are A gap is provided between them, and a cylindrical flexible seal member is provided inside the seal member in advance (hereinafter, the former seal member is referred to as “first seal member”, and the latter seal member is referred to as “second seal”). In addition, a cylindrical adapter is fitted inside the second seal member, and the adapter is fixed to the inner peripheral surface of the cooling liquid outlet through an O-ring to enhance the sealing performance. Thought.

  That is, according to this configuration, when the rotary valve device is closed, the coolant in the rotor housing space of the housing passes through the gap between the outer peripheral surface of the first seal member and the inner peripheral surface of the coolant outlet. The second seal member is reached. Then, the second seal member is elastically deformed toward the adapter side due to the liquid pressure of the coolant that has reached the second seal member, and the contact pressure between the second seal member and the adapter is increased, and the sealing performance between these is increased. The second seal member is pressed toward the rotor while being secured. Since the second seal member is pressed toward the rotor side, the resultant force of the pressing force due to the hydraulic pressure and the elastic force of the elastic member acts on the first seal member as a force for pressing the first seal member toward the rotor side. The sealing performance between the first seal member and the rotor can be enhanced.

  However, in the above method of increasing the sealing performance by applying the coolant pressure toward the rotor side, a gap is provided between the first seal member and the coolant outlet, and therefore the assembly work of the valve device When the first seal member is disposed in the coolant outlet, it is difficult to align (align) the center of the coolant outlet with the center of the first seal member. As described above, when the center of the coolant outlet and the center of the first seal member do not coincide with each other, it becomes difficult to fit the adapter inside the second seal member, and the assembling property of the adapter is lowered. In addition, the contact pressure between the rotor and the first seal member is not uniform over the entire circumferential direction of the first seal member, and the sealing performance between the rotor and the first seal member may be reduced. Further, the contact pressure between the adapter and the second seal member is not uniform over the entire circumferential direction of the second seal member, and the sealing performance between the adapter and the second seal member may be reduced. For this reason, there is a possibility that the flow rate control of the coolant cannot be performed appropriately.

  Therefore, when enhancing the sealing performance by utilizing the liquid pressure of the coolant, it is necessary not to impair the assembling workability of the valve device.

  Accordingly, the present invention is an engine coolant control valve device that is provided in a coolant flow path that connects an engine and an auxiliary machine, and that controls the flow rate of the coolant in the flow path. A rotor having a circular section in section, a housing space for rotatably housing the rotor, a housing having at least two second openings connected to the housing space and connected to the flow path, and the first A cylindrical first seal member that is inserted into the second opening in a state having a gap between the inner periphery of the two openings, and a tip portion of which is in sliding contact with the outer peripheral surface of the rotor; and the first seal member In contact with the inner peripheral surface of the second seal member, an elastic member that urges the rotor toward the rotor, a second seal member that is provided inside the first seal member, and has an annular cross section. Inner peripheral surface of the second opening A cylindrical portion that is inserted into the second opening in a state of being spaced apart from the cylindrical portion, and extends radially outward from the cylindrical portion to be fixed to an inner peripheral surface of the second opening. A flange that forms a fluid pressure acting space that communicates with the housing space through the gap and causes the fluid pressure of the coolant to act on the second seal member between the inner peripheral surface of the opening and the cylindrical portion. An insertion member having a portion, and abutting from the outside of the first seal member at a plurality of circumferential positions on the outer peripheral surface of the first seal member, and the first seal member to the second opening An engine coolant control valve device including a positioning unit for positioning is provided.

  According to the present invention, the coolant that has flowed into the housing from the first opening of the rotor flows into the hydraulic pressure working space through the gap between the outer peripheral surface of the first seal member and the inner peripheral surface of the second opening. To do. Since the hydraulic pressure of the coolant flowing into the hydraulic pressure space presses the flexible second seal member toward the rotor side and the cylindrical portion side, the second seal member moves the first seal member toward the rotor side. The pressure is increased to increase the contact pressure between the first seal member and the outer peripheral surface of the rotor, and the contact pressure between the second seal member and the cylindrical portion is increased by deformation to the cylindrical portion side. As a result, the sealing performance between the first seal member and the rotor and the sealing performance between the second seal member and the cylindrical portion can be enhanced, so that the valve closed state (the first opening of the rotor and the housing In a state in which the second opening does not overlap, the coolant can be prevented from flowing into the insertion member from the rotor, and the coolant flow rate can be appropriately controlled.

  Furthermore, since the positioning part which positions a 1st seal member with respect to a 2nd opening part is provided, when assembling the valve apparatus which concerns on this invention, a 1st seal member is made into an appropriate position in a 2nd opening part. It can be easily positioned. That is, a gap is provided between the outer peripheral surface of the first seal member and the inner peripheral surface of the second opening in order to introduce the coolant into the hydraulic pressure action space. Since the first seal member is easily positioned in the second opening and the first seal member is disposed at an appropriate position, the second seal provided inside the first seal member is provided. The insertion member can be easily and properly inserted into the member, the assembling property of the inserting member is improved, and as a result, the assembling workability of the valve device is improved. Furthermore, since the positioning portion is provided in a state of contacting with a plurality of positions in the circumferential direction on the outer peripheral surface of the first seal member, a gap through which the coolant passes is ensured between the contact portions adjacent to each other. The positioning part does not hinder the inflow of the coolant into the hydraulic pressure action space.

  In the present invention, the positioning portion has a plurality of protrusions extending in the axial direction of the second opening at a plurality of positions in the circumferential direction and abutting on the outer peripheral surface of the first seal member. Is preferred.

  According to this configuration, the outer peripheral surface of the first seal member can be supported in a more stable state by the plurality of protrusions. Furthermore, since each protrusion serves as a guide when the first seal member is inserted into the second opening, insertion of the first seal member into the second opening can be performed smoothly.

  In the present invention, the rotor is preferably formed in a hollow and spherical shape.

  According to this structure, the front-end | tip part of the 1st seal member which slidably contacts with the outer peripheral surface of a rotor can be formed in circular shape. Thereby, the contact pressure between the first seal member and the rotor can be made uniform over the entire circumferential direction of the first seal member, and higher and more stable sealing performance can be ensured.

  In this invention, it is preferable that the said 2nd sealing member is integrally provided inside the said 1st sealing member.

  According to this configuration, since the hydraulic pressure of the coolant acting on the second seal member is reliably transmitted to the first seal member, the sealing performance between the first seal member and the rotor can be further enhanced.

  As described above, according to the present invention, an engine coolant control that can ensure a higher level of sealing performance and more appropriately control the coolant flow rate while ensuring good assembly workability. A valve device can be obtained.

1 is a diagram showing an engine cooling system (a state immediately after the start of a warm-up operation) to which an engine coolant control valve device according to an embodiment of the present invention is applied. FIG. 2 is a diagram showing a state in which a heater is operating during a warm-up operation of the engine cooling system shown in FIG. 1. It is a figure which shows the state after the warming-up completion of the engine cooling system shown by FIG. It is sectional drawing which shows the coolant control valve apparatus of the engine which concerns on embodiment of this invention. It is sectional drawing which expands and shows the principal part in FIG. 4 (it cut | disconnects in the position of a protrusion part). It is sectional drawing which expands and shows the principal part in FIG. 4 (it cut | disconnects in positions other than a rib part). It is a figure which shows the state before attaching a 1st seal member etc. to the 2nd opening part by the side of the radiator of the coolant control valve apparatus shown by FIG. 4, (a) is the outline seen from A direction of (b) FIG. 4B is a cross-sectional view seen from the engine side. (A) is an exploded sectional view showing a state before the first seal member or the like is assembled to the second opening on the radiator side of the coolant control valve device shown in FIG. It is sectional drawing which shows a sealing member and a 2nd sealing member. It is sectional drawing which shows the mode (radiator side) in the assembly operation | work of the cooling fluid control valve apparatus shown by FIG. FIG. 5 is an exploded cross-sectional view showing a state before the first seal member or the like is assembled to the second opening on the heater core side of the coolant control valve device shown in FIG. 4. FIG. 5 is an exploded cross-sectional view showing a state before the first seal member or the like is assembled to the second opening on the heater core side of the coolant control valve device shown in FIG. 4.

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

  1 to 3 schematically show the rotary valve device 2 in a developed state (functionally).

  As shown in FIGS. 1 to 3, the engine 3 in the present embodiment includes a cylinder block 3 </ b> A and a cylinder head 3 </ b> B provided on the upper side of the cylinder block 3 </ b> A (shown on the lower side in FIG. 1). .

  1 to 3 show the cylinder block 3A and the cylinder head 3B as viewed from above.

  1 to 3, when an arrow is written in the flow path of the cooling water (corresponding to “cooling liquid” of the present invention), this means that the cooling water is flowing through the flow path. When an arrow is not described on the path, it indicates that cooling water is not flowing through the flow path.

  As shown in FIGS. 1 to 3, a plurality of cylinders # 1 to # 4 into which pistons (not shown) are fitted are formed in the cylinder block 3A and the cylinder head 3B, respectively. 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 3 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 (corresponding to the “cooling fluid control valve device” of the present invention) 2 described later is provided at the end of the cylinder head 3B on the fourth cylinder # 4 side. The engine 3 is arranged in an engine room provided in the front part of the vehicle.

  The cylinder block 3A has a main water jacket 13 provided around the cylinders # 1 to # 4. A main water jacket (hereinafter referred to as a “block side flow path”) 13 passes through the cylinder block 3A so as to make a round from the first cylinder # 1 side to the fourth cylinder # 4 side to the first cylinder # 1 side. To do. The upstream end of the block side flow path 13 is connected to a discharge port of an engine side pump 4 described later.

  A main water jacket 14 is formed on the cylinder head 3B. A main water jacket (hereinafter referred to as “head-side flow path”) 14 passes in the cylinder row direction from the first cylinder # 1 side to the fourth cylinder # 4 side through a portion around the combustion chamber. The upstream end of the head side flow path 14 is connected to the downstream end of the block side flow path 13, and the downstream end of the head side flow path 14 is connected to the rotary valve device 2.

  Next, the cooling system 1 for the engine 3 will be described.

  As shown in FIGS. 1 to 3, the cooling system 1 of the engine 3 includes a cooling water circulation path 60, a radiator 6, water temperature sensors 23 and 24, an intake air temperature sensor 9, a crank angle sensor 10, and an accelerator. The opening degree sensor 11, the heater side pump 22, the engine side pump 4, the rotary valve apparatus 2, and ECU8 (Electronic Control Unit) are provided.

  The circulation path 60 is a path through which the cooling water circulates. The block side flow path 13, the head side flow path 14, the radiator side flow path 20, the return flow path 17, the heater side flow path 18, the ATF side flow path 19, the water temperature. It has a detection flow path 16 and a communication flow path 21.

  The radiator-side flow path 20 is a flow path that passes through the radiator 6 (included in the “auxiliary machine” of the present invention). The upstream end of the radiator side flow path 20 is connected to the rotary valve device 2, and the downstream end of the radiator side flow path 20 is connected to the return flow path 17.

  The return flow path 17 is a flow path for returning the cooling water flowing out from the radiator side flow path 20, the water temperature detection flow path 16, the heater side flow path 18, and the ATF side flow path 19 to the engine side pump 4. The downstream end of the radiator side flow path 20, the water temperature detection flow path 16, the heater side flow path 18, and the ATF side flow path 19 is connected to the upstream portion or middle flow portion of the return flow passage 17. The downstream end of the return flow path 17 is connected to the suction port of the engine side pump 4.

  The heater-side flow path 18 is a flow path that passes through the heater core 5 of the air conditioner (included in the “auxiliary machine” of the present invention). The upstream end of the heater side flow path 18 is connected to the rotary valve device 2.

  The ATF (Automatic Transmission Fluid) side flow path 19 is a flow path that passes through the ATF warmer 7 (included in the “auxiliary machine” of the present invention). The upstream end of the ATF side channel 19 is connected to a section between the heater side pump 4 and the rotary valve device 2 in the heater side channel 18.

  The communication flow path 21 is a flow path that connects a thermostat 45 (described later) and the radiator-side flow path 20 in the rotary valve device 2. The upstream end of the communication channel 21 is connected to the downstream side of the thermostat 45, and the downstream end of the communication channel 21 is connected to the downstream side of the radiator 6 in the radiator side channel 20.

  The water temperature sensor 23 is provided in the water temperature detection flow path 16 and detects the temperature of the cooling water immediately after flowing out of the rotary valve device 2. The water temperature sensor 24 is provided on the downstream side of the radiator 6 in the radiator-side flow path 20 and detects the temperature of the cooling water flowing out from the radiator 6. The intake air temperature sensor 9 detects the temperature of intake air flowing into the engine 3. The crank angle sensor 10 detects the rotation angle of the crankshaft. The accelerator opening sensor 11 detects the amount of depression of the accelerator pedal by the driver as the accelerator opening.

  The ECU 8 is constituted by a CPU, a RAM, a ROM, and the like. The ECU 8 controls operations of the rotary valve device 2 and the heater-side pump 22 based on signals indicating detection values received from the water temperature sensor 23, the intake air temperature sensor 9, the crank angle sensor 10, and the accelerator opening sensor 11. And the control signal is transmitted to the rotary valve device 2 and the heater side pump 22.

  The heater side pump 22 is an electronically controlled electric pump. The heater-side pump 22 is provided on the upstream side of the heater core 5 in the heater-side flow path 18 described later.

  The engine-side pump 4 is a mechanical pump and operates upon receiving the driving force of the engine 3.

  As shown in FIGS. 1 to 3, the rotary valve device 2 is provided in a cooling water flow path connecting the engine 3 and the auxiliary machines 5, 6, 7, and controls the flow rate of the cooling water in the flow path. It is. Specifically, a cooling water intake (a second opening 36c described later) of the rotary valve device 2 is connected to the downstream end of the head-side flow path 14, and four cooling water discharge ports (described later) of the rotary valve device 2 are connected. The second openings 36a, 36b, 36d, and 36e) are connected to the upstream ends of the radiator side flow path 20, the heater side flow path 18, the water temperature detection flow path 16, and the communication flow path 21, respectively.

  As shown in FIG. 4, the rotary valve device 2 includes a rotary shaft 32, a hollow and spherical rotor 33 that rotates together with the rotary shaft 32, a housing 30 that rotatably accommodates the rotor 33, and the rotary shaft 32. An electronically controlled electric motor (not shown) that rotates the rotor 33, a first seal member 38, a second seal member 39, an elastic member 42, insertion members 37 and 44, and a thermostat 45 are provided. ing.

  The rotor 33 includes a spherical peripheral wall portion 33g, a hollow portion 33f surrounded by the inner wall surface of the peripheral wall portion 33g, and a plurality of spoke portions 31 that extend radially from the rotation shaft 32 and support the peripheral wall portion 33g from the inside.

  The peripheral wall 33g (the outer peripheral surface of the rotor 33) has five first openings 33a to 33e (see FIG. 1). The five first openings 33a to 33e communicate with each other through the hollow portion 33f.

  The first of the five first openings is a first opening 33a (see FIGS. 1 and 4) located on the side of the rotating shaft 32, and the second is located on the side of the rotating shaft 32. And the 2nd opening part 33b (refer FIG.1, 4) provided adjacent to the 1st opening part 33a in the circumferential direction of the rotating shaft 32, and the 3rd-5th are the electric motor in the rotating shaft 32, and Are first openings 33c, 33d, 33e (see FIG. 1) provided in the vicinity of the opposite end.

  As shown in FIGS. 4 and 7 to 11, the housing 30 is surrounded by a hollow and spherical housing space side outer wall portion 36 </ b> A and an inner wall surface of the housing space side outer wall portion 36 </ b> A, and houses the rotor 33 rotatably. It is formed in the space 36f, the flow channel side outer wall portion 36B formed integrally with the accommodation space side outer wall portion 36A, and the flow channel side outer wall portion 36B. The inner end communicates with the accommodation space 36f and the flow channel 14 is formed at the outer end portion. , 16, 18, 20, and 21 have five second openings 36a to 36e (see FIG. 1).

  The first of the five second openings is a second opening 36a (see FIGS. 1-4, 7 and 8) to which the upstream end of the radiator-side flow path 20 is connected, and the second is a heater. The second opening 36b (see FIGS. 1 to 4 and 10) to which the upstream end of the side channel 18 is connected, and the third is the second opening to which the downstream end of the head side channel 14 is connected. Part 36c (see FIGS. 1 to 3), and the fourth is a second opening 36d (see FIGS. 1 to 3) to which the upstream end of the water temperature detection flow path 16 is connected, and the fifth is The second opening 36e (see FIGS. 1 to 4) to which the upstream end of the communication channel 21 is connected. A thermostat 45 (see FIGS. 1 to 4) is provided in the second opening 36e.

  The thermostat 45 has a water temperature sensor and a valve device (not shown). When the temperature detected by the water temperature sensor exceeds a predetermined temperature, the valve device is opened (see FIG. 3), and the temperature detected by the water temperature sensor is the predetermined temperature. If it is less, the valve device is closed (see FIGS. 1 and 2). When the valve device is opened, the second opening 36e is opened and communicates with the first opening 33e, and when the valve device is closed, the second opening 36e is closed and the second opening 36e is closed. The first opening 33e is not in communication.

  The second opening 36 a is in communication or non-communication with the first opening 33 a depending on the rotation angle of the rotor 33. That is, when the second opening 36a and the first opening 33a overlap, the second opening 36a and the first opening 33a are in communication, and the second opening 36a and the first opening 33a do not overlap. And the 2nd opening part 36a and the 1st opening part 33a will be in a non-communication state.

  The second opening 36b is in communication or non-communication with the first opening 33b depending on the rotation angle of the rotor 33. That is, when the second opening 36b and the first opening 33b overlap, the second opening 36b and the first opening 33b are in communication with each other, and the second opening 36b and the first opening 33b do not overlap. And the 2nd opening part 36b and the 1st opening part 33b will be in a non-communication state.

  The second opening 36 c is always in communication with the first opening 33 c regardless of the rotation angle of the rotor 33. Regardless of the rotation angle of the rotor 33, the second opening 36d is always in communication with the first opening 33d.

  A gap 36g (see FIGS. 5 and 6) is provided between the inner wall surface of the housing space side outer wall portion 36A and the outer peripheral surface of the peripheral wall portion 33g.

  The first seal member 38, the second seal member 39, and the elastic member 42 are disposed in the second openings 36a and 36b, respectively. The arrangement state of these members in the second opening 36a, and the first The arrangement state in the two openings 36b is substantially the same. First, the arrangement | positioning state in the 2nd opening part 36a of these members is demonstrated.

  The first seal member 38 is inserted into the second opening 36 a with a gap 43 (see FIG. 6) between the first opening 36 a and the inner peripheral surface of the second opening 36 a, and the tip portion slides on the outer peripheral surface of the rotor 33. It is a cylindrical member in contact.

  As shown in FIG. 8B, the first seal member 38 includes an annular slidable contact portion 38a in which the tip end portion on the rotor 33 side slidably contacts the outer peripheral surface of the rotor 33, and an anti-rotor side of the slidable contact portion 38a. It is a member having an annular holding portion 38b that extends from the radially outer portion of the surface to the opposite rotor side and holds the second seal member 39 on the inner peripheral surface. The cross section along the radial direction of the first seal member 38 is annular, and the cross section along the axial direction is L-shaped. The material of the first seal member 38 is not particularly limited. For example, the first seal member 38 is made of a synthetic resin such as PTFE (polytetrafluoroethylene).

  As shown in FIG. 8B, the second seal member 39 has an annular held portion 39a whose outer peripheral surface is held (fitted and fixed) by the holding portion 38b of the first seal member 38, and the held portion. This is a member having an annular contact portion 39b that extends obliquely inward from the end portion on the rotor 33 side of 39a toward the opposite rotor side and contacts the outer peripheral surface of the insertion member 37. The cross section along the radial direction of the second seal member 39 is annular, and the cross section along the axial direction is V-shaped. The material of the second seal member 39 is not particularly limited. For example, the second seal member 39 is made of a flexible material (elastic material) such as rubber.

  The second seal member 39 is fitted and fixed in advance to the first seal member 38 before being inserted into the second opening 36a (see FIG. 8A).

  The elastic member 42 is a member that biases the first seal member 38 toward the rotor 33, and is formed in a cylindrical shape. For example, as illustrated in FIG. 8A, the elastic member 42 is configured by a spring that can expand and contract in the axial direction of the second opening 36 a. The elastic member 42 shown in FIG. 8A is configured by combining a plurality of leaf springs formed in a wave shape. The end of the elastic member 42 on the rotor 33 side is in contact with the end of the first seal member 38 (holding portion 38 b) on the side opposite to the rotor, and the end of the elastic member 42 on the side opposite to the rotor is described later of the insertion member 37. Abutting against the flange portion 37a.

  As shown in FIGS. 5 and 6, the insertion member 37 is a cylindrical member having a cylindrical portion 37b and a flange portion 37a, and has a through-hole 37A extending from one end portion in the axial direction to the other end portion. ing.

  The cylindrical portion 37b is in contact with the inner peripheral surface of the second seal member 39 and is spaced from the inner peripheral surface 360 (see FIGS. 6 and 8) of the second opening portion 36a in the second opening portion 36a. Inserted.

  The flange portion 37a extends radially outward from the cylindrical portion 37b and is fixed to the inner peripheral surface of the second opening portion 36a. An O-ring 37d is externally fitted to the flange portion 37a. The flange portion 37a is fixed to the inner peripheral surface 360 of the second opening portion 36a by the O-ring 37d, and the flange portion 37a and the second opening portion 36a. Is sealed between the inner peripheral surface 360 (see FIGS. 5 and 6).

  The flange portion 37a forms a hydraulic pressure acting space 37c between the inner peripheral surface of the second opening 36a and the cylindrical portion 37b (see FIGS. 5 and 6). The hydraulic pressure working space 37c includes an inner peripheral surface 360 of the second opening 36a, a surface of the flange portion 37a on the rotor 33 side, an outer peripheral surface of the cylindrical portion 37b, and a surface of the second seal member 39 on the side opposite to the rotor. And an annular space surrounded by the opposite surface of the first seal member 38 and communicates with the accommodation space 36f through the gap 43 (see FIG. 6). The hydraulic pressure working space 37 c causes the hydraulic pressure of the coolant introduced through the gap 43 to act on the second seal member 39. Specifically, the cooling water introduced into the hydraulic pressure working space 37c presses the first seal member 38 and the second seal member 39 toward the rotor 33 and inserts the contact portion 39b of the second seal member 39. Press toward the member 37 side. As a result, the contact pressure between the first seal member 38 and the outer peripheral surface of the rotor 33 is increased, the sealing performance between the first seal member 38 and the rotor 33 is improved, and the second seal member 39 and the insertion member 37 are improved. The contact pressure between the second seal member 39 and the insertion member 37 is ensured.

  As shown in FIG. 7, the inner peripheral surface 360 of the second opening 36 a extends in the axial direction of the second opening 36 a and is first in four circumferential positions on the outer peripheral surface of the first seal member 38. Four protrusions (corresponding to the “positioning portion” of the present invention) 361 that contact the outer side of the seal member 38 and position the first seal member 38 with respect to the second opening 36 a are formed.

  The protruding portion 361 protrudes radially inward from the inner peripheral surface of the second opening 36a, and the tip portion in the protruding direction contacts the outer peripheral surface of the first seal member 38 (see FIGS. 5 and 7). The four ridges 361 are arranged at substantially equal intervals in the circumferential direction.

  The gap 43 is secured between the inner peripheral surface of the second opening 36a (the portion where the protrusion 361 is not formed) and the outer peripheral surface of the first seal member 38 (see FIG. 6). ).

  By these four protrusions 361, the first seal member 38 is positioned in the second opening 36a and fixed in the second opening 36a. The four protrusions 361 function as slide guides when the first seal member 38 is inserted into the second opening 36a.

  Next, the arrangement state of the first seal member 38, the second seal member 39, and the elastic member 42 in the second opening 36b will be described.

  As shown in FIGS. 4, 10, and 11, a cylindrical insertion member 44 that is integrally provided at the tip of the heater-side flow path 18 is inserted into the second opening 36 b instead of the insertion member 37. Is done. As shown in FIG. 4, the insertion member 44 is a cylindrical member having a cylindrical portion 44b and a flange portion 44a, and has a through hole 44A extending from one end portion in the axial direction to the other end portion. ing. The insertion member 44 is integrally formed with the same material as the heater-side channel 18 at the tip of the heater-side channel 18.

  The cylindrical portion 44b is inserted into the second opening 36b in contact with the inner peripheral surface of the second seal member 39 and spaced from the inner peripheral surface of the second opening 36b.

  The flange portion 44a extends radially outward from the tubular portion 44b and is fixed to the inner peripheral surface of the second opening 36b. An O-ring 44d is externally fitted to the flange portion 44a. The flange portion 44a is fixed to the inner peripheral surface of the second opening portion 36b by the O-ring 44d, and the flange portion 44a and the second opening portion 36b. The space between the inner peripheral surface is sealed.

  The flange portion 44a forms a hydraulic pressure space 44c similar to the hydraulic pressure space 37c between the inner peripheral surface of the second opening 36b and the cylindrical portion 44b.

  As shown in FIG. 4, the inner surface of the second opening 36 b extends in the axial direction of the second opening 36 b and has a first seal at four circumferential positions on the outer surface of the first seal member 38. Four protrusions (corresponding to the “positioning part” in the present invention) 362 for positioning the first seal member 38 with respect to the second opening 36 b are formed in contact with the outside of the member 38.

  The protruding portion 362 protrudes radially inward from the inner peripheral surface of the second opening 36 b, and the tip portion in the protruding direction contacts the outer peripheral surface of the first seal member 38. The four ridges 362 are arranged at substantially equal intervals in the circumferential direction.

  A gap (not shown) is provided between the inner peripheral surface of the second opening 36 b (the portion where the protrusion 362 is not formed) and the outer peripheral surface of the first seal member 38.

  By these four protrusions 362, the first seal member 38 is positioned in the second opening 36b and fixed in the second opening 36b. The four protrusions 362 function as slide guides when the first seal member 38 is inserted into the second opening 36b.

  Next, the effect of the rotary valve device 2 according to the present embodiment will be described.

  The detected value of the water temperature sensor 24 is used to determine whether or not the radiator 6 is functioning properly while the rotary valve device 2 and the heater-side pump 22 are controlled by the ECU 8. In the following description, the description of the control operation of the rotary valve device 2 and the heater side pump 22 using the detection value of the water temperature sensor 24 is omitted.

  Based on the detection results of the intake air temperature sensor 9, the crank angle sensor 10, the accelerator opening sensor 11, and the water temperature sensor 23, the state of the engine 3 is determined by the ECU 8. Then, according to the determination result, the ECU 8 controls the opening and closing of the valves with respect to the respective flow paths of the rotary valve device 2.

  Specifically, when it is determined that the coolant temperature is low immediately after the engine is started, the ECU 8 does not overlap the through hole 37A of the insertion member 37 and the first openings 33a and 33b of the rotor 33, In addition, the rotation angle of the rotor 33 is controlled so that the first seal member 38 in the vicinity of the insertion member 37 contacts the outer peripheral surface of the rotor 33 (see FIG. 4). As a result, the rotary valve device 2 is closed with respect to the radiator-side flow path 20, and the cooling water does not flow through the radiator-side flow path 20 (see FIGS. 1 and 2). Further, in the ECU 8, the through hole 44 </ b> A of the insertion member 44 and the first openings 33 a and 33 b of the rotor 33 do not overlap with each other, and the first seal member 38 in the vicinity of the insertion member 44 contacts the outer peripheral surface of the rotor 33. The rotation angle of the rotor 33 is controlled to the state (see FIG. 4), and the heater-side pump 22 is stopped. As a result, the rotary valve device 2 is closed with respect to the heater side flow path 18, and cooling water does not flow through the heater side flow path 18 and the ATF side flow path 19 (see FIG. 1). By not supplying cooling water to the radiator side flow path 20, the heater side flow path 18, and the ATF side flow path 19, warm-up of the engine 3 is promoted.

  In a state where the valve is closed with respect to the radiator-side flow path 20, the cooling water flows into the hydraulic pressure working space 37 c through the gap 43, and the cooling water presses the first seal member 38 and the second seal member 39. Since the hydraulic pressure of the cooling water flowing into the hydraulic pressure working space 37c presses the flexible second seal member 39 toward the rotor 33 and the cylindrical portion 37b, the second seal member 39 is an elastic member 42. In cooperation with the first seal member 38, the first seal member 38 is pressed toward the rotor 33 to increase the contact pressure between the first seal member 38 and the outer peripheral surface of the rotor 33, and the second seal member is deformed toward the cylindrical portion 37b. The contact pressure between 39 and the cylindrical portion 37b is increased. Thereby, since the sealing performance between the 1st seal member 38 and the rotor 33 and the sealing performance between the 2nd seal member 39 and the cylindrical part 37b can be improved, a cooling water is a rotor in a valve closing state. Inflow from 33 to the cylindrical portion 37b can be prevented, and the flow rate control of the cooling water can be appropriately performed.

  Furthermore, since the protrusion part 361 which positions the 1st seal member 38 with respect to the 2nd opening part 36a is provided, when assembling the rotary valve apparatus 2, the 1st seal member 38 in the 2nd opening part 36a. Can be easily positioned at an appropriate position. That is, a gap 43 is provided between the outer peripheral surface of the first seal member 38 and the inner peripheral surface of the second opening 36a in order to introduce the cooling water into the hydraulic pressure acting space 37c. In the embodiment, since the protruding portion 361 is provided, the positioning of the first seal member 38 in the second opening 36a is facilitated, and the first seal member 38 is disposed at an appropriate position. The insertion member 37 can be easily and properly inserted into the second seal member 39 provided inside the first seal member 38, and the assembling property of the insertion member 37 is improved. As a result, the rotary valve device 2 is assembled. Workability will be good.

  Furthermore, since the protrusion 361 is provided in contact with a plurality of circumferential positions on the outer peripheral surface of the first seal member 38, the gap 43 through which the cooling water passes between the adjacent contact portions. Is secured, and the protrusion 361 does not hinder the flow of cooling water into the hydraulic pressure acting space 37c.

  Further, the outer peripheral surface of the first seal member 38 can be stably supported by the plurality of protrusions 361 extending in the axial direction of the second opening 36a at a plurality of positions in the circumferential direction. Furthermore, since each protrusion 361 serves as a guide when the first seal member 38 is inserted into the second opening 36a, the insertion operation of the first seal member 38 into the second opening 36a is smoothly performed. (See FIGS. 8 and 9).

  Further, since the rotor 33 is formed in a hollow and spherical shape, the tip end portion of the first seal member 38 that is in sliding contact with the outer peripheral surface of the rotor 33 can be formed in a circular shape. Thereby, the contact pressure between the first seal member 38 and the rotor 33 can be made uniform over the entire circumferential direction of the first seal member 38, and stable sealing performance can be ensured.

  Further, since the second seal member 39 is integrally provided inside the first seal member 38, the coolant pressure acting on the second seal member 39 is reliably transmitted to the first seal member 38, The sealing performance between the first seal member 38 and the rotor 33 can be enhanced.

  The same effect as that of the hydraulic pressure space 37c is also generated in the hydraulic pressure space 44c. Furthermore, the same effect as that of the protrusion 361 is also generated in the protrusion 362.

  When a certain amount of time has elapsed from the start of the engine and the water temperature of the cooling water has increased to some extent, and the heater switch (not shown) is turned on, the ECU 8 connects the radiator valve 20 to the radiator side flow path 20. While maintaining the valve closed state, the rotation angle of the rotor 33 is controlled so that the through hole 44A of the insertion member 44 and the first opening 33b of the rotor 33 overlap with each other, and the heater side pump 22 is operated. As a result, the rotary valve device 2 is opened with respect to the heater-side channel 18, and as a result, cooling water flows through the heater-side channel 18 and the ATF-side channel 19 (see FIGS. 2 and 3). By flowing cooling water that has been heated to some extent through the heater-side flow path 18, the air in the passenger compartment can be warmed through the heater core 5.

  Further, when it is determined that the temperature of the cooling water has reached a predetermined temperature and the warm-up operation has been completed, the ECU 8 is inserted while maintaining the valve open state with respect to the heater-side flow path 18 of the rotary valve device 2. The rotation angle of the rotor 33 is controlled so that the through-hole 37A of the member 37 and the first opening 33a of the rotor 33 overlap each other. As a result, the rotary valve device 2 is opened with respect to the radiator-side flow path 20, and as a result, cooling water flows through the radiator-side flow path 20 (see FIG. 3). The engine 3 is cooled by the cooling water flowing through the radiator-side flow path 20.

  In the above embodiment, the rotor 33 is formed in a hollow and spherical shape. However, the present invention is not limited to this, and the rotor 33 may be formed in a cylindrical shape.

  Moreover, in the said embodiment, although the four protrusion parts 361 and 362 are each provided, it is not restricted to this, You may provide 3 or 5 or more respectively. In any case, the protrusions 361 and 362 are provided at substantially equal intervals in the circumferential direction.

  Moreover, in the said embodiment, although the positioning part of this invention is comprised by four protrusions protruding inside from the inner wall face of a 2nd opening part, it is not restricted to this, For example, a 2nd opening part A cylindrical portion that is inserted in a state where it abuts against the inner peripheral surface of the second opening, and an axial direction of the second opening at a plurality of positions in the circumferential direction that protrudes inward from the inner peripheral surface of the cylindrical portion The positioning portion may be constituted by a spacer member (not shown) that has a plurality of protrusions that extend to the outer periphery of the first seal member and abut against the outer peripheral surface of the first seal member.

2 Rotary valve device 3 Engine 5 Heater core (auxiliary machine)
6 Radiator (auxiliary machine)
7 ATF warmer (auxiliary machine)
16 Water temperature detection flow path 17 Return flow path 18 Heater side flow path 19 ATF side flow path 20 Radiator side flow path 21 Connection flow path 30 Housing 33 Rotor 33a to 33e First opening 36a to 36e Second opening 37, 44 Insertion member 37a, 44a Flange part 37b, 44b Cylindrical part 37c, 44c Hydraulic action space 38 First seal member 39 Second seal member 42 Elastic member 43 Gap 361, 362 Projection part

Claims (4)

A coolant control valve device for an engine that is provided in a coolant flow path connecting the engine and the auxiliary device and controls the flow rate of the coolant in the flow path,
A rotor having an annular cross section having a first opening on the outer peripheral surface;
A housing that rotatably accommodates the rotor, and a housing that communicates with the housing space and has at least two second openings to which the flow path is connected;
A cylindrical first seal member that is inserted into the second opening in a state having a gap with the inner peripheral surface of the second opening, and the tip end portion is in sliding contact with the outer peripheral surface of the rotor;
An elastic member for urging the first seal member toward the rotor;
A second seal member provided on the inner side of the first seal member and having a flexible cross section in cross section;
A cylindrical portion that is in contact with the inner peripheral surface of the second seal member and is spaced from the inner peripheral surface of the second opening portion, and a diameter from the cylindrical portion. Extending outward in the direction and fixed to the inner peripheral surface of the second opening, and communicated with the accommodating space through the gap between the inner peripheral surface of the second opening and the cylindrical portion. An insertion member having a flange portion that forms a hydraulic pressure acting space that causes the hydraulic pressure of the second sealing member to act on the second seal member;
A positioning portion that contacts from the outside of the first seal member at a plurality of circumferential positions on the outer peripheral surface of the first seal member and positions the first seal member with respect to the second opening. Engine coolant control valve device.   The positioning portion has a plurality of protrusions extending in the axial direction of the second opening at a plurality of positions in the circumferential direction and abutting on the outer peripheral surface of the first seal member, The engine coolant control valve device according to claim 1.   The engine coolant control valve device according to claim 1, wherein the rotor is formed in a hollow and spherical shape.   4. The engine coolant control valve device according to claim 1, wherein the second seal member is integrally provided inside the first seal member. 5.

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