JP2019085942A - Valve device - Google Patents

Abstract

To provide a valve device which can suppress a pressure loss of fluid, and is compact in a size.SOLUTION: A valve device comprises a turning valve VA, a thermostat valve Vb and a housing 4 having a fluid flow-in port 41 which is opened and closed by the turning valve Va and the thermostat valve Vb. The thermostat valve Vb is accommodated in the housing 4 in a posture in which a valve part 31a linearly moves along a direction vertical to a turning shaft 5, the flow-in port 41 communicates with one flow passage, the flow-in port 41 is defined by a first flow-in port 41A which can be opened and closed by the turning valve Va, and a second flow-in port 41B which can be opened and closed by the thermostat valve Vb, and a flow passage of the first flow-in port 41A and a flow passage of the second flow-in port 41B are arranged in parallel with each other.SELECTED DRAWING: Figure 5

Description

  The present invention relates to a valve device provided with a thermostat valve.

  Conventionally, there is known a valve device in which a thermostat valve as a main control valve and an electromagnetic control type poppet valve as a sub control valve are housed in a housing in a cooling path connecting an engine and a radiator (for example, Patent Document 1) reference).

  The valve device described in Patent Document 1 includes a first-class inlet which can be opened and closed by a thermostat valve having a first valve portion which linearly moves the inflow port of cooling water provided in the housing, and a second valve portion which linearly moves. A second inlet port that can be opened and closed by an electromagnetic control type poppet valve is provided, and the respective valves are arranged in parallel. It is described that this can prevent overheating even if one of the valves fails. Further, in the electromagnetic control type poppet valve, the second valve portion is perpendicular to the flow direction of the fluid (the straight movement direction of the first valve portion) because the electromagnetic portion as the drive source is not provided in the flow path. It is configured to move straight.

JP 10-317967 A

  Since the valve device described in Patent Document 1 uses the electromagnetic control type poppet valve as the sub control valve, the space for the second valve portion to move in a straight line must be provided perpendicularly to the flow direction of the fluid. It does not. As a result, in order to secure a desired opening area at the time of valve opening, it is necessary to increase the stroke length of the second valve portion, and it is necessary to increase the driving force of the electromagnetic portion, and the second valve portion in the housing The moving space of the valve also becomes large, and the entire valve device becomes large. In addition, since the straight movement direction of the first valve portion and the second valve portion is vertical, the flow path of the first-class inlet and the flow path of the second inflow port become vertical, and the flow path configuration becomes complicated. Pressure loss will increase.

  Therefore, a compact valve device capable of suppressing fluid pressure loss is desired.

  Characteristic features of the valve device include a rotary valve having a rotary shaft driven by a drive source, a valve body rotating in conjunction with the rotary shaft, and a thermal expansion body that expands or contracts at the temperature of the fluid. A thermostat valve having a temperature sensing portion accommodated therein, a valve portion linearly moving by operation of the temperature sensing portion, an inlet and outlet for fluid opened and closed by the rotary valve and the thermostat valve, and a fluid from the inlet And a housing for containing the rotary valve and the thermostat valve, and the thermostat valve moves the valve portion linearly along a direction perpendicular to the rotary shaft. It is housed in the housing in such a posture, the inflow port is in communication with one flow path, and the inflow port can be opened and closed by the first-class inlet which can be opened and closed by the pivot valve, and the thermostat valve Second inlet A is partitioned, the flow path of the first inlet and said second inlet flow passage is in that it is arranged parallel.

  The valve device in this configuration includes a pivoting valve having a valve body that pivots interlockingly with the pivoting shaft, and a thermostat valve having a valve portion that linearly moves along a direction perpendicular to the pivoting shaft. There is. That is, since the valve body of the rotary valve rotates without moving in a straight line, even if the rotary shaft is disposed in a direction perpendicular to the linear movement direction of the valve portion of the thermostat valve, the valve body of the rotary valve There is no need to secure a large stroke length. As a result, it is possible to minimize the movement space of the valve body while reducing the driving force of the driving source, and the entire valve device can be made compact.

  Moreover, in the present configuration, the inlet is partitioned by a first-class inlet that can be opened and closed by a pivoting valve and a second inlet that can be opened and closed by a thermostat valve, and the flow path of the first-tiered inlet and the second inlet And the flow paths of are arranged in parallel. For this reason, when the first-class inlet is opened by the rotary valve and the second inlet is opened by the thermostat valve, the respective flow paths are in the same direction, thereby minimizing the fluid pressure loss. be able to.

  Thus, the compact valve device which can control the pressure loss of fluid was able to be provided.

  Another feature is that the flow rate of the fluid flowing through the first leading inlet when the pivoting valve is fully open is set larger than the flow rate of the fluid flowing through the second inlet when the thermostat valve is fully opened It is in the point being done.

  The pressure loss of the fluid moves the valve straight in the same direction as the fluid flow direction because the pivoting valve opens and closes the first-class inlet by pivoting the valve body in the direction intersecting the fluid flow direction. Small compared to the thermostat valve. As in this configuration, if the flow rate when the rotation valve is fully open is larger than the flow rate when the thermostat valve is fully open, the rotation valve may be the main control valve and the thermostat valve may be the sub control valve. It becomes possible. That is, under the situation where a desired flow rate is required, the fluid can be smoothly circulated in a state where the pressure loss is small.

  Another feature is that the first-class inlet is provided downstream of the second inlet.

  As in this configuration, by providing the first-class inlet downstream of the second inlet, the fluid flowing to the first-class inlet passes through the second inlet. That is, compared to the case where the first-class inlet is provided on the upstream side of the second inlet, the flow rate passing through the second inlet can be increased, and the temperature-sensitive performance of the thermostat valve can be improved. Moreover, since the flow path of the thermostat valve is shortened, the pressure loss of the fluid passing through the thermostat valve can be reduced.

  Another characteristic configuration is that the valve body is formed with a hole facing the first-class inlet when the rotary valve is in the open state, and the valve body faces the second inlet. When the rotary valve is in the closed state, the hole is opposed to the second inlet.

  As in the present configuration, since the hole faces the second inlet when the rotary valve is in the closed state, the fluid flowing through the thermostat valve is smoothly transferred to the outlet of the housing through the hole. It can be distributed. In addition, since the second inlet is not blocked by the valve when the pivoting valve is in the open state, the pressure loss when the thermostat valve is in the open state is reduced, and the flow rate flowing to the outlet can be increased. .

  Another feature is that the housing further includes a third inlet for communicating fluid toward the temperature sensing unit and at least in communication with a heater path in which the heater core is disposed.

  As in the present configuration, when the fluid is caused to flow from the heater path to the temperature sensing unit, the temperature characteristics of the fluid can be accurately reflected, so that the temperature sensing performance of the temperature sensing unit can be improved.

It is a schematic diagram of the cooling system which has arrange | positioned the valve apparatus. It is a top view of a valve device. It is a bottom view of a valve device showing a state when a rotation valve is closed. It is the IV-IV sectional view taken on the line of FIG. FIG. 5 is a cross-sectional view taken along line V-V of FIG. 4 in which the rotation valve is in the open state and the thermostat valve is in the open state. FIG. 5 is a cross-sectional view taken along line V-V of FIG. 4 in which the rotation valve is in a closed state and the thermostat valve is in a closed state.

  Below, an embodiment of a valve device concerning the present invention is described based on a drawing. In the present embodiment, as an example of the valve device, a valve device V used in a cooling system of an engine E for a car will be described. However, without being limited to the following embodiments, various modifications can be made without departing from the scope of the invention.

  As shown in FIG. 1, the cooling system of the engine E includes a cooling path 1 for circulating cooling water (an example of a fluid) between the engine E and the radiator R, and a heater core H for generating warm air in the engine E and the vehicle. And a water pump P for supplying the cooling water to the engine E, and a connecting pipeline 10 for connecting the valve device V to the engine E, which will be described later.

  The cooling passage 1 passing through the radiator R and the heater passage 2 passing through the heater core H are connected to the water pump P by the connecting conduit 10 via the valve device V. The cooling path 1 cools the cooling water heated by the engine E by the radiator R, and then returns the cooling water to the engine E through the valve device V. Heater path 2 arranges on-off valve 3 between engine E and heater core H, and when the on-off valve 3 is in the open state, heater core is heated to warm the air in the passenger compartment with the cooling water heated by engine E. Make it flow into H. At this time, the cooling water heat-exchanged and cooled by the heater core H is returned to the engine E via the valve device V.

  On the other hand, when the cooling water is lower than the predetermined temperature, the on-off valve 3 is closed so that the cooling water is not circulated in the heater path 2, thereby preventing a decrease in the temperature of the cooling water due to heat exchange in the heater core H. Further, when the temperature of the cooling water is low, the valve device V provided with a thermostat valve Vb described later is also closed, so the cooling water is not circulated to the radiator R as well. For this reason, temperature rise of the cooling water at the time of warm-up operation of engine E can be promoted, and improvement in fuel consumption can be aimed at.

(Basic configuration)
As shown in FIGS. 2 to 6, the valve device V includes a pivoting valve Va, a thermostat valve Vb, and a housing 4 that accommodates the pivoting valve Va and the thermostat valve Vb (see FIG. 5).

  The rotary valve Va is supported by the negative pressure actuator K (an example of a drive source) and the housing 4 and is perpendicular to the rotary shaft 5 and the rotary shaft 5 rotated by receiving the driving force from the negative pressure actuator K And a valve body 6 that rotates integrally with the rotation shaft 5 (in conjunction with the rotation shaft 5) (see FIG. 4).

  The negative pressure actuator K is configured to move a rod (not shown) by pulling a diaphragm (not shown) by negative pressure, and to rotate the pivot shaft 5 by a link mechanism (not shown) connected to the rod. It is done. A motor is used as a drive source to drive the pivot shaft 5, or the pivot shaft 5 is pivoted by a link mechanism connected to a plunger of an electromagnetic solenoid. Also, it is not particularly limited.

  The housing 4 has an inlet 41 for receiving the cooling water and an outlet 42 from which the cooling water from the inlet 41 flows out. A first flange portion 41a protruding in the radial direction is formed in the inflow port 41, and the first flange portion 41a is connected to the flange portion 1a provided on the radiator R side in the cooling path 1 described above (See Figure 5).

  The inlet 41 in the present embodiment is constituted by a first-class inlet 41A which can be opened and closed by the valve body 6 of the rotary valve Va, and a second inlet 41B which can be opened and closed by the thermostat valve Vb. The first inlet 41A and the second inlet 41B are partitioned inside the housing 4 in communication with one flow passage of the cooling path 1, and are arranged in parallel so as to be parallel to each other. Further, the housing 4 is provided with a third inlet 41C communicating with the heater path 2 (see FIG. 2). The flow passage of the third inlet 41C is formed in parallel with the direction of the pivot shaft 5, and the flow passage of the first inlet 41A and the second inlet 41B and the flow passage of the third inlet 41C are orthogonal to each other. There is. The flow passage of the first-class inlet 41A and the flow passage of the second inlet 41B may be arranged in parallel in a state where they are not parallel to each other and have predetermined crossing angles.

  A radially projecting second flange portion 42 a is formed at the outlet 42, and the second flange portion 42 a is connected to a flange portion (not shown) provided on the valve device V side in the connecting conduit 10. (See Figure 3). Since the flow passage of the outflow port 42 is formed in the direction of the pivot shaft 5, it is orthogonal to the flow paths of the first inlet 41A and the second inflow port 41B, and the flow path of the third inflow port 41C Are formed in parallel.

  Further, in the housing 4, a hollow cylindrical support portion 43 for supporting the pivot shaft 5 is formed between the inflow port 41 and the outflow port 42 (see FIG. 4). A radially outwardly recessed annular step 43a is formed on the inner surface of the support portion 43, and a first seal S1 and a bearing 43b are formed between the annular step 43a and the pivot shaft 5. It is provided. An inner surface 44 of the housing 4 formed in a plane region perpendicular to the pivot shaft 5 is configured by an arc region 44a having a predetermined curvature and a linear region 44b (see FIG. 3).

  The valve body 6 is pivoted integrally with the pivot shaft 5 along the plane perpendicular to the pivot shaft 5 (in conjunction with the pivot shaft 5). The valve body 6 includes a fixing portion 61 fixed to one end of the pivot shaft 5, a plurality of (three in the present embodiment) extending portions 62 extending radially from the fixing portion 61, and an extending portion 62 And the curved wall portion 63 which is pivoted along the arc region 44a by connecting the extended ends of the two (see FIGS. 3 to 4). The extension portion 62 is formed in a trapezoidal shape in a side view which widens from the connection portion with the fixing portion 61 to the connection portion with the curved wall portion 63. The curved wall portion 63 has a surface area capable of closing the first-class inlet 41 A, and is formed in an arc shape in a cross section in a direction perpendicular to the pivot shaft 5. In addition, as a form which the valve body 6 rotates interlockingly with the rotational axis 5, instead of integrally comprising the fixing portion 61, the extension portion 62 and the curved wall portion 63, for example, A biasing member may be provided between the curved wall 63 and the curved wall 63 to bias the curved wall 63 toward the arc area 44a.

  The curved wall portion 63 is formed between the pair of extending portions 62, and is formed between the hole portion 63a having an opening area slightly smaller than the opening area of the first inlet 41A and the other pair of extending portions 62. And a closed portion 63b having a surface area larger than the opening area of the first inlet 41A (see FIGS. 4 to 6). When the rotary valve Va in a state in which the entire area of the opening of the hole 63a overlaps the first-class inlet 41A is fully open (the state of FIG. 4 and FIG. 5), the second contact abuts on the periphery of the hole 63a A seal S2 projects from the first inlet 41A into the interior space of the housing 4.

  In the first-class inlet 41A, the third seal S3 disposed adjacent to the second seal S2, the second seal S2 and the third seal S3 are urged toward the curved wall portion 63 of the valve body 6 A coil spring 11 is disposed. One end of the coil spring 11 is in contact with the stepped portion 1 b formed on the flange portion 1 a of the cooling path 1, and one end of the second seal S 2 is in contact with the curved wall 63 of the valve body 6. That is, the coil spring 11, the second seal S2, and the third seal S3 are supported in a state of being sandwiched between the step portion 1b of the cooling path 1 and the curved wall portion 63 of the valve body 6, and constitute a sealing mechanism. doing.

  By this sealing mechanism, when the rotary valve Va is fully open (the states of FIGS. 4 and 5), the cooling water from the first inlet 41A does not leak to the side of the hole 63a, and the hole 63a Through the outlet 42. On the other hand, when the rotary valve Va in which the closed portion 63b is overlapped with the first-class inlet 41A is fully closed (state in FIG. 6), the cooling water from the first-class inlet 41A flows into the internal space of the housing 4. It is intercepted without doing.

  The thermostat valve Vb has a movable body 31 to which an annular valve portion 31a is fixed, a spring 32 which biases the movable body 31, and a support frame 33 which is fixed to the housing 4 and supports the movable body 31. (See FIGS. 5 to 6). The thermostat valve Vb is fixed to the housing 4 in such a posture that the valve portion 31 a moves rectilinearly in a direction perpendicular to the rotation shaft 5. The movable body 31 has a temperature sensitive portion 31c that accommodates a thermal expansion body (such as wax) that causes pressure to act on a pressure receiving surface (not shown) of the piston 31b by expanding or contracting due to a temperature change of the cooling water. The coolant from the third inlet 41C communicating with the heater path 2 flows through the temperature sensing portion 31c.

  When the temperature of the cooling water flowing through the thermostat valve Vb becomes equal to or higher than a predetermined temperature (for example, 85 ° C.), the thermal expansion body expands, and a force moving toward the end of the support frame 33 acts on the piston 31 b. At this time, since the support frame 33 and one end of the piston 31 b are fixed to the housing 4, the pressure due to the expansion of the thermal expansion body acts on the pressure receiving surface of the other end of the piston 31 b, and the movable body 31 compresses the spring 32. Move in the direction Thereby, the valve portion 31a fixed to the movable body 31 is separated from the support frame 33, and the thermostat valve Vb is opened (see FIG. 5). On the other hand, when the temperature of the cooling water flowing to the thermostat valve Vb becomes lower than the predetermined temperature, the thermal expansion body contracts, and the valve portion 31a fixed to the movable body 31 moves close to the support frame 33 and the thermostat valve Vb Close the valve (see FIG. 6). As described above, the flow path of the third inlet 41C that causes the cooling water to flow into the temperature sensing portion 31c is formed in parallel with the direction of the rotation shaft 5, and the valve portion 31a of the thermostat valve Vb is the temperature sensing portion By the operation of 31 c, it moves back and forth along the direction perpendicular to the pivot shaft 5.

  In the present embodiment, the flow rate through the first inlet 41A when the rotary valve Va is fully open is set larger than the flow rate through the second inlet 41B when the thermostat valve Vb is fully open (see FIG. 5). Specifically, when the rotary valve Va is fully open, the flow passage cross-sectional area of the first inlet 41A is set larger than the flow passage cross-sectional area of the second inlet 41B when the thermostat valve Vb is fully open. ing. Thus, in the present embodiment, the pivoting valve Va is a main control valve, and the thermostat valve Vb is a sub control valve. As a result, in a situation where a predetermined flow rate is required, it is possible to reliably cool the cooling water by securing a flow rate flowing through the rotation valve Va with a small pressure loss. On the other hand, even when the rotary valve Va fails, the overheat of the engine E can be prevented by opening the thermostat valve Vb.

  Further, in the present embodiment, the first inlet 41A is provided downstream of the second inlet 41B (see FIG. 5). As a result, a part of the cooling water directed to the first-class inlet 41A passes through the second inlet 41B, so that the flow rate through the second inlet 41B is secured to improve the temperature-sensitive performance of the thermostat valve Vb. Can. Moreover, since the flow path of the thermostat valve Vb is shortened as compared with the flow path of the rotary valve Va, the pressure loss of the cooling water passing through the thermostat valve Vb can be reduced.

  In the present embodiment, as shown in FIG. 5, when the rotary valve Va is in the open state, the valve body 6 is formed with a hole 63a facing the first inlet 41A and the second inlet 41B. The valve body 6 does not face to. As a result, the pressure loss when the thermostat valve Vb is in the open state is reduced, and the flow rate flowing to the outlet 42 can be increased. Further, as shown in FIG. 6, when the rotary valve Va is in the closed state, the closed portion 63b faces the first inlet 41A, and the hole 63a faces the second inlet 41B. Thus, the cooling water flowing from the heater path 2 through the thermostat valve Vb via the third inlet 41C can be smoothly circulated to the outlet 42 of the housing 4 via the hole 63a.

Other Embodiments
(1) The flow rate through the first inlet 41A when the rotation valve Va is fully open may be set smaller than the flow rate through the second inlet 41B when the thermostat valve Vb is fully open. . In this case, the thermostat valve Vb is used as a main control valve, and the rotation valve Va is functioned as a sub control valve.

(2) The first inlet 41A may be provided upstream of the second inlet 41B. In this case, since the cooling water can be caused to flow preferentially through the first-class inlet 41A, the cooling performance when the pivoting valve Va is used as the main control valve can be enhanced.

(3) When the rotary valve Va is in the open state, the hole 63a of the valve body 6 is opposed to the first-class inlet 41A, and the closed portion 63b of the valve 6 is opposed to the second inlet 41B to rotate. When the valve Va is in the closed state, the closed portion 63b of the valve 6 may be opposed to the first inlet 41A, and the valve 6 may not be opposed to the second inlet 41B. In this case, the arrangement of the hole 63a and the closing portion 63b shown in FIG. 3 is reversed.

(4) The heater path 2 may be provided in parallel with an oil cooler or an EGR cooler that cools oil such as ATF.

(5) The valve device V is not limited to the case where it is used for the cooling system of the engine E for automobiles, and may be used for the engine oil circulation system.

  The present invention is applicable to a valve device provided with a thermostat valve.

Reference Signs List 2 heater path 4 housing 5 rotary shaft 6 valve body 31a valve portion 31c temperature sensing portion 41 inlet 41A first inlet 41B second inlet 41C third inlet 42 outlet 63a hole K negative pressure actuator (drive source)
V valve device Va rotation valve Vb thermostat valve

Claims (5)

A pivoting valve having a pivoting shaft driven by a drive source and a valve body pivoting in conjunction with the pivoting shaft;
A thermostatic valve having a temperature sensitive section containing a thermal expansion body that expands or contracts at the temperature of the fluid, and a valve section that linearly moves by operation of the temperature sensitive section;
It has an inlet for fluid opened and closed by the rotary valve and the thermostat valve, and an outlet from which the fluid from the inlet flows out, and the housing accommodates the rotary valve and the thermostat valve. ,
The thermostat valve is accommodated in the housing in such a posture that the valve portion linearly moves in a direction perpendicular to the rotation axis,
The inlet is in communication with one flow passage, and the inlet is divided into a first-class inlet which can be opened and closed by the rotary valve, and a second inlet which can be opened and closed by the thermostat valve. A valve device in which the flow passage of the first inlet and the flow passage of the second inlet are arranged in parallel.   The flow rate of the fluid flowing through the first inlet when the rotary valve is fully open is set larger than the flow rate of the fluid flowing through the second inlet when the thermostat valve is fully opened. The valve device according to.   The valve device according to claim 1, wherein the first inlet is provided downstream of the second inlet. When the rotary valve is in the open state, the valve body is formed with a hole facing the first-class inlet, and the valve body does not face the second inlet,
The valve device according to any one of claims 1 to 3, wherein the hole faces the second inflow port when the pivot valve is in a closed state.   The valve device according to any one of claims 1 to 4, wherein the housing further includes a third inlet that communicates fluid toward the temperature sensing unit and communicates with at least a heater path in which a heater core is disposed.

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