JP2013011225A - Flow controller - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flow controller 3 that meets severe requirements for downsizing, weight reduction, cost reduction and the like by arranging a poppet valve part and a rotary valve part in series to synergistically use the advantages of both valve parts, as a flow control mechanism of cooling water which flows through a cooling circuit of a prime mover.SOLUTION: Valve bodies 30, 31 are each set in valve body cases 24, 25 installed in the cooling circuit of a prime mover. With a direction changing means (cam grooves 30g, 31g and pin members 32, 33) installed to displace the valve bodies 30, 31 in the axial direction in addition to the rotation direction by driving (displacing in the rotation direction) the valve bodies 30, 31 with a motor 13. The axial direction displacement of the valve bodies 30, 31 gives the function of the poppet valve part, whereas the rotation direction displacement of the valve bodies 30, 31 gives the function of the rotary valve part. The downsizing, weight reduction and cost reduction of the whole device are thus achieved by using the characteristics of both valve parts.

Description

  The present invention relates to a flow rate control device that is disposed in a cooling circuit of a prime mover such as an internal combustion engine mounted on an automobile and controls a flow rate of a cooling medium that circulates through the cooling circuit.

(Conventional technology)
As an internal combustion engine of an automobile (hereinafter referred to as an engine), a water-cooled engine using cooling water as a cooling medium is widely used, and a cooling device (cooling circuit) for circulating the cooling water has various configurations. However, as the performance of automobiles increases, types that can control the cooling efficiency of the engine with high accuracy according to the operating conditions of the engine have become mainstream.
As a typical example, in a cooling device as shown in Patent Document 1, an engine cooling circuit is constituted by two cooling water passages, a water jacket on the cylinder head side and a water jacket on the cylinder block side. At the same time, in the cooling water passage of each system, an attempt is made to optimize the cooling water temperature by adjusting the radiator flow rate passing through the radiator and the bypass flow rate bypassing the radiator and passing through the bypass passage according to the operating state of the engine. To do.

  In the cooling device, a flow rate control device is provided in each of the two cooling water passages. In this flow rate control device, a DC motor is used as a drive source, and the rotation is conical with a screw spline mechanism. A poppet valve type valve mechanism that controls the flow rate by converting it to body stroke (axial displacement), and a rotary valve type valve that uses a step motor as the drive source to control the flow rate by displacing the rotary valve body in the rotational direction. The mechanism is adopted.

(Problems of conventional technology)
However, since the valve mechanisms of the flow rate control device are all based on the basic concept of driving a single valve with a single drive source, three-way control in each cooling water passage is realized with the same drive source. For this purpose, the relationship between the valve body and the three-way passage opened and closed by the valve body is naturally limited, and is not suitable for high-precision flow rate control.
In addition, two sets of cooling water passages require two sets of flow control devices, and the installation in a narrow space around the engine is becoming increasingly severe.

In addition, the individual valve systems themselves of the valve mechanism have the following problems.
The poppet type is inevitably long in the axial direction in order to obtain a desired control stroke, and is considerably restricted in terms of mounting surface.
In addition, the rotary valve type employs a so-called clearance seal in which the watertight seal between the outer peripheral surface of the valve body and the inner peripheral surface on the valve body support side is in sliding contact with each other. The leakage of the cooling water cannot be minimized due to the leakage of water from the gap, leading to a decrease in engine operation efficiency and an increase in warm-up time. Of course, in order to minimize the leakage of cooling water, measures to press the rotary valve with rubber or resin are also considered, but the drive torque increases, requiring a large physique for the motor as the drive source, There are problems in terms of mounting and cost.

JP 62-247112 A

  The above problems are especially fatal in the current situation where the demands for smaller, lighter and lower costs for equipment mounted on automobiles are increasingly severe. There is an urgent need for a solution that responds to strict requirements such as cost.

  The present invention has been made to solve the above-mentioned problems, and its purpose is to make use of both the poppet valve function and the rotary valve function so that their characteristics are synergistic, thereby reducing the size, weight, and The purpose of this invention is to provide a flow control device suitable for a cooling device for a prime mover in response to severe demands such as cost reduction.

[Means of Claim 1]
According to the flow control device employing the means of claim 1, a housing having a first port and a second port connected to a cooling circuit of a prime mover (eg, engine) and inputting / outputting a cooling medium (eg, cooling water). In this valve body storage chamber, the valve body for intermittently communicating the first and second ports is stored so that axial displacement and rotational displacement are possible. Then, a drive source that drives the valve body in either one of the axial direction or the rotational direction, and the valve body is driven in one direction by the drive source, so that the valve body is either in the axial direction or the rotational direction. Direction change means for displacing in the direction, and the first flow rate control unit is configured by the one end face in the axial direction of the valve body and the first port, and the circumferential surface in the circumferential direction of the valve body and the second A second flow rate control unit is configured with the port, the first flow rate control unit is controlled to open and close by the axial displacement of the valve body, and the second flow rate control unit is controlled to open and close by the rotational direction displacement of the valve body. It is characterized by that.

  As a result, the first flow control unit can be used as a poppet valve function, and the second flow control unit can be used as a rotary valve function to realize flow control utilizing the characteristics of each valve function. Since the double-valve function can be activated by the drive source, the flow control device can be made small, light, and inexpensive.

[Means of claim 2]
According to the flow control device adopting the means of claim 2, the first valve in the housing having the first port and the second port connected to the cooling circuit of the prime mover for inputting / outputting the cooling medium is provided in the first chamber. The valve body for intermittently communicating the second port is similar to the means of claim 1 in that the valve body is housed so as to be capable of axial displacement and rotational displacement, but the valve body is used as a drive source. Driven in the rotational direction, and means for displacing the valve body in the axial direction when the valve body is driven in the rotational direction by a drive source is used as the direction changing means. The first flow rate control unit is configured by the one end surface in the axial direction of the valve body and the first port, and the second flow rate control unit is configured by the circumferential surface of the valve body in the circumferential direction and the second port. The first flow rate control unit is controlled to open / close by the axial displacement of the valve body, and the second flow rate control unit is controlled to open / close by the rotational direction displacement of the valve body.

  With such a configuration, a motor is used as a drive source, and the same effect as the means of claim 1 can be obtained. In addition, by using a motor as a drive source, two valve mechanisms can be driven by the same motor even in the case of two-system cooling in which a valve mechanism is provided in each cooling system.

[Means of claim 3]
According to the flow control device employing the means of claim 3, when the valve body is driven by the drive source, the second flow control unit opens after the first flow control unit opens. Yes.
With such a configuration, the characteristics of the first flow rate control unit, that is, the poppet valve with high sealing performance can be fully utilized to realize a completely shut-off state of the cooling circuit. The flow rate can be minimized. Thus, the engine warm-up time can be shortened and the temperature of the engine main body can be maintained high, which contributes to efficient operation.

[Means of claim 4]
According to the flow rate control device employing the means of claim 4, the first flow rate control unit includes a face seal formed by one end surface of the valve body and a receiving surface of the valve body storage chamber with which the one end surface abuts in the axial direction. The second flow rate control unit is characterized in that a clearance seal is formed by a gap between the peripheral surface of the valve body and the peripheral surface of the valve body storage chamber with which the peripheral surface is in sliding contact. It is said.
With such a configuration, a necessary seal can be secured in the poppet valve part of the first flow rate control unit, and the seal of the rotary valve unit of the second flow rate control unit can be a simple clearance seal. The driving torque can be reduced and the driving source can be further reduced in size.

[Means of claim 5]
According to the flow control device adopting the means of claim 5, the valve body has a first opening and a second opening that communicate with each other inside thereof and open to the peripheral surface side of the valve body, respectively. The first opening communicates with the first port when the valve body is axially displaced to the valve opening position, and the second opening is second when the valve body is displaced in the rotational direction by a predetermined amount. It is characterized by communicating with other ports.
According to such a configuration, two functions of a poppet valve function and a rotary valve function can be obtained with one valve body, and the valve body itself can be configured with a cylindrical body that can be easily manufactured.

[Means of claim 6]
According to the flow control device employing the means of claim 6, the direction changing means is provided in the valve body storage chamber and the valve body, and is constituted by a pin member and a cam groove which are engaged with each other. Yes.
According to such a configuration, the two valve portions of the poppet valve portion and the rotary valve portion can be efficiently controlled by a single drive source with a simple structure of the pin member and the cam groove.

[Means of Claim 7]
According to the flow control device adopting the means of claim 7, the valve body storage chamber is provided with the urging means for urging the valve body toward the one end surface side. The axial restriction between the pin member and the cam groove is released when the flow control unit is in the valve closing position.
According to this configuration, when the first flow rate control unit is closed, the urging force of the urging means can be used as the sealing force of the poppet valve unit. Further, by releasing the restriction in the axial direction, the valve closing position of the valve body can be automatically determined, and a simple drive that does not require precise control can be used as a drive source.

[Means of Claim 8]
According to the flow control device adopting the means of claim 8, the first port is connected to the cooling medium supply side of the cooling circuit, and the pressure adjustment communicates the one end surface side and the other end surface side of the valve body. It is characterized by a passage.
With such a configuration, the pressure of the cooling medium can be utilized as a pressing force from the other end surface side to the one end surface side of the valve body, that is, a sealing force.

[Means of Claim 9]
According to the flow control device adopting the means of claim 9, the valve element is characterized in that the pressure receiving area on one end side is set smaller than the pressure receiving area on the other end side.
Thereby, the sealing force by the means of Claim 8 can further be raised.

[Means of Claim 10]
According to the flow control device adopting the means of claim 10, the cam groove also serves as a part of the pressure adjusting passage.
With such a configuration, the structure can be made more compact.

1 is a system diagram schematically showing an overall configuration of a water-cooled engine cooling device to which a flow control device of the present invention is applied. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a perspective view schematically illustrating an exploded overall configuration of a flow control device of the present invention (Example 1). It is a perspective view which expands and shows the single-piece | unit structure of the principal part in FIG. FIG. 3 is a schematic cross-sectional view of a valve portion for explaining the operation of the flow control device of the present invention. It is a typical longitudinal section of a valve part used for operation explanation of a flow control device of the present invention.

  The best mode for carrying out the present invention will be described in detail with reference to the following examples.

[Example 1]
This embodiment shows an example in which the flow control device of the present invention is applied to a cooling device for a water-cooled engine mounted on an automobile. First, the overall configuration of the engine cooling circuit will be described with reference to FIG. .

The water-cooled engine 1 is a kind of prime mover that uses cooling water as a cooling medium, and includes a first cooling water passage 1a that passes through a water jacket on the cylinder head side and a second cooling that passes through a water jacket on the cylinder block side. Two cooling water passages with the water passage 1b are provided.
One end of each of the cooling water passages 1 a and 1 b branches from the discharge side of the water pump 2, and the other end passes through the flow rate control device 3 and the radiator passage 4 and the first and second bypass passages, respectively. After branching to the bypass passage 7 made up of 5 and 6, it is a closed loop in which it joins again on the suction side of the water pump 2. A cooling circuit 8 of the engine 1 is constructed by this closed loop cooling water passage.
Therefore, when the water pump 2 is driven by the engine 1, the cooling water circulates through the cooling circuit 8 to cool the engine 1.

The flow rate control device 3 controls the flow rate of cooling water in two systems, and includes a valve mechanism 12 substantially consisting of two valves 10 and 11, and a motor 13 that is a drive source for driving the valves 10 and 11. The basic structure is a command device 14 that controls energization of the motor 13 in accordance with the operating state of the engine 1. In particular, the specific structure of the valve mechanism 12 that forms the main part of the present invention will be described in detail later. To do.
The valves 10 and 11 have a three-way valve function, and the first passages 10a and 11a are connected to the first and second cooling water passages 1a and 1b, respectively, and the second passages 10b and 11b are bypass passages. 7 are connected to the first and second bypass passages 5 and 6, respectively, and the third passages 10 c and 11 c merge to be connected to the radiator passage 4.
Thus, the flow rate control device 3 appropriately controls the flow rate of the cooling water circulating through the cooling circuit 8 of the engine 1 based on the command from the command device 14.

  The radiator passage 4 is provided with a radiator 15 that is disposed in front of the automobile and that controls the heat radiation of the cooling water. In the bypass passage 7, first and second heat exchangers 16 and 17 are provided in the first and second bypass passages 5 and 6, respectively.

Next, a specific configuration of the flow control device 3 will be described with reference to FIGS. 2, 3, and 5, the illustrated vertical relationship is referred to as “up” and “down” for convenience.
The valve mechanism 12 and the motor 13 are generally composed of components shown in FIGS.
The flow control device 3 has a housing 20, and the housing 20 is composed of three parts including a valve body 21 having a cylindrical shape as a whole, a disc-shaped inner lid 22, and a cap-shaped outer lid 23. The valve body 21 forming the center is provided with first and second valve body storage chambers 24 and 25 in parallel in the axial direction. A motor 13 having a drive shaft 13a is attached and fixed to an axial recess 21a formed on the outer periphery of the valve body 21 by an attachment stay 13b or the like.

As shown in FIG. 5, the valve body storage chambers 24 and 25 have a blind hole shape with a circular cross section having bottom portions 24a and 25a, and the bottom portions 24a and 25a have first passages 10a and 11a. One port 24b, 25b is formed.
Further, as shown in FIG. 4, connecting pipes 26 and 27 forming the second passages 10b and 11b and connecting pipes 28 and 29 forming the third passages 10c and 11c are opposed to the outer peripheral surface of the valve body 21. So as to protrude. These connecting pipes 26 to 29 are opened as second ports 24c and 25c and third ports 24d and 25d on the inner peripheral surfaces of the valve body storage chambers 24 and 25, respectively.
The valve body storage chambers 24 and 25 include first ports 24b and 25b on the cooling water input side, second ports 24c and 25c on the cooling water output side, and third ports 24d and 25d. As a means for interrupting the communication, the first and second valve bodies 30 and 31 are accommodated in the valve body accommodating chambers 24 and 25.

The valve bodies 30 and 31 have a two-stage cylindrical shape as a whole. The valve bodies 30 and 31 have small diameter portions 30a and 31a on the lower side and large diameter portions 30b and 31b on the upper side, respectively. 25 is accommodated so as to be slidable (displaceable) in both the axial direction and the rotational direction. The valve bodies 30 and 31 have bottom plate portions 30c and 31c in the small diameter portions 30a and 31a. The lower end surfaces (one axial end surfaces) of the bottom plate portions 30c and 31c are the bottom portions of the valve body storage chambers 24 and 25. The first ports 24b and 25b are closed by contacting (sitting) with the upper end surfaces (receiving surfaces) of 24a and 25a. Thus, the poppet valve portion P that constitutes the first flow rate control portion is configured.
The small diameter portions 30 a and 31 a of the valve bodies 30 and 31 have an outer diameter smaller than the inner diameter of the valve body storage chambers 24 and 25 and are loosely fitted in the valve body storage chambers 24 and 25.

Further, the small-diameter portions 30a and 31a of the valve bodies 30 and 31 are provided with window portions (first opening portions) 30d and 31d that open on the outer peripheral surface, and the large-diameter portions 30b and 31b of the valve bodies 30 and 31 are provided on the large-diameter portions 30b and 31b. Window portions (second opening portions) 30e and 31e that open to the outer peripheral surface are provided. The window portions 30d and 31d of the small diameter portions 30a and 31a and the window portions 30e and 31e of the large diameter portions 30b and 31b communicate with each other through a hollow portion formed in the central portion of the valve bodies 30 and 31 themselves.
The large diameter portions 30b and 31b of the valve bodies 30 and 31 are in sliding contact with the inner peripheral surfaces of the valve body storage chambers 24 and 25, and open and close the second ports 24c and 25c and the third ports 24d and 25d. Thereby, the rotary valve part R which comprises a 2nd flow control part is comprised.

  Longitudinal grooves 30f and 31f extending in the axial direction and cam grooves 30g and 31g extending in the circumferential direction are provided on the outer peripheral surfaces of the large diameter portions 30b and 31b of the valve bodies 30 and 31, respectively. The vertical grooves 30f and 31f form a pressure adjusting passage, and the lower end communicates with the outer peripheral side of the small diameter portions 30a and 31a, and the upper end communicates with the cam grooves 30g and 31g. A pair of guide grooves 30h and 31h extending straight in the axial direction are provided at both end portions of the cam grooves 30g and 31g.

The pin members 32 and 33 engaged with the cam grooves 30g and 31g are fixed to mounting holes 24e and 25e provided on the upper end side (inlet side) of the valve body storage chambers 24 and 25, respectively. By engaging the pin members 32 and 33 and the cam grooves 30g and 31g, the valve bodies 30 and 31 are raised in the axial direction while rotating at the initial stage of rotation, and then displaced only in the circumferential direction. Cam profiles of cam grooves 30g and 31g are set. Thus, the cam grooves 30g, 31g and the pin members 32, 33 constitute a direction changing means.
When the pin members 32 and 33 are positioned in the guide grooves 30h and 31h, the valve bodies 30 and 31 can move freely in the axial direction with respect to the pin members 32 and 33, so The axial restraint is released.

The drive bodies 34 and 35 transmit the rotation of the motor 13 to the valve bodies 30 and 31, and are configured as two-stage shafts. The lower-stage large-diameter shaft portions 34a and 35a fitted into the valve bodies 30 and 31 are provided. And small-diameter shaft portions 34b, 35b on the upper stage side that slidably support the spring receiving plates 36, 37. The upper ends of the small-diameter shaft portions 34b and 35b are serrations 34c and 35c.
The lower large-diameter shaft portions 34a and 35a are non-rotatably coupled to the valve bodies 30 and 31 by the key X and the key groove Y, and the upper small-diameter shaft portions 34b and 35b are fixed to the fixed spring receiver 38. , 39 and the axially movable spring receiving plates 36, 37, compression type springs (biasing means) that press the spring receiving plates 36, 37 against the upper end surfaces of the large diameter shaft portions 34a, 35a. 40 and 41 are provided.
The spring receiving plates 36 and 37 have an outer diameter slightly smaller than the inner diameters of the valve body storage chambers 24 and 25, and slide (slid on the inner peripheral surfaces of the valve body storage chambers 24 and 25 in both the axial direction and the rotation direction. Notch portions 36a and 37a are provided in part of the outer peripheral portion corresponding to the guide grooves 30h and 31h of the valve bodies 30 and 31.

  The components from the valve body 30, 31 to the drive bodies 34, 35 are sequentially stored in the valve body storage chambers 24, 25, and the inner lid 22 is attached and fixed to the valve body 21 by attachment means such as screws. Thus, the two valves 10 and 11 having both functions of the poppet valve portion P and the rotary valve portion R are completed.

In the small diameter shaft portions 34b and 35b of the driving bodies 34 and 35, the serrations 34c and 35c pass through the holes 22a and 22b of the inner lid 22, and the serrations 34c and 35c are coupled to the large gears 42 and 43. Similarly, the drive shaft 13 a of the motor 13 also passes through the hole 22 c of the inner lid 22 and is coupled to the small gear 44 that meshes with the large gears 42 and 43. Therefore, the rotation of the motor 13 is decelerated by the speed reduction mechanism including the gears 42 to 44 and is transmitted from the driving bodies 34 and 35 to the valve bodies 30 and 31.
Further, the speed reduction mechanism including the gears 42 to 44 is housed in the outer lid 23 that is fixedly attached to the inner lid 22 by attaching means such as screws, and is dust-proof.

In the flow control device 3 having the above-described configuration, the characteristic configuration of the valve mechanism 12 (two valves 10 and 11) constituting the main part will be supplementarily described below.
In the initial setting state, the pin members 32 and 33 are positioned in the guide grooves 30h and 31h, and the axial restriction by the direction changing means is released. For this reason, the valve bodies 30 and 31 are configured so that the bottom plate portions 30c and 31c of the small diameter portions 30a and 31a are bottom portions of the valve body storage chambers 24 and 25 through the spring receiving plates 36 and 37 by the biasing force of the springs 40 and 41. 24a and 25a are pressed. That is, the lower end surfaces (one axial end surface) of the bottom plate portions 30c and 31c are seated in pressure contact with the upper end surfaces (receiving surfaces) of the bottom portions 24a and 25a of the valve body storage chambers 24 and 25, respectively. 24b and 25b are closed. This state is a closed state of the poppet valve portion P that constitutes the first flow rate control portion. In this embodiment, when the valve is closed, a water-tight structure is formed by flat sealing between the end faces. However, the both end faces may be formed as conical faces.

  On the other hand, at this time, the large diameter portions 30b and 31b of the valve bodies 30 and 31 close the second ports 24c and 25c and the third ports 24d and 25d, and the outer peripheral surfaces of the large diameter portions 30b and 31b and the valve A watertight structure is formed by a clearance seal formed by a minute gap with the inner peripheral surfaces of the body storage chambers 24 and 25. Therefore, the rotary valve portion R that forms the second flow rate control portion is also closed.

When the valve bodies 30 and 31 are driven by the motor 13 and start to rotate, the valve bodies 30 and 31 are engaged with the pin members 32 and 33 and the cam grooves 30g and 31g in the initial stage of the rotation. It rises in the axial direction against the springs 40 and 41 according to the cam profile. Due to this axial displacement, the bottom plate portions 30c, 31c of the small diameter portions 30a, 31a are separated from the bottom portions 24a, 25a of the valve body storage chambers 24, 25, while the large diameter portions 30b, 31b are connected to the second port 24c, 25c and the third ports 24d and 25d are kept closed. That is, the poppet valve portion P opens, but the rotary valve portion R remains closed.
Thereafter, when the valve bodies 30 and 31 are further rotated, the large diameter portions 30b and 31b open the second ports 24c and 25c and the third ports 24d and 25d, and the rotary valve portion R is opened. . Thereafter, the flow rate of the cooling water passing through the second ports 24c and 25c and the third ports 24d and 25d is changed by changing the opening area of the rotary valve portion R according to the rotation of the valve bodies 30 and 31. Can be controlled.

  Once the poppet valve portion P is opened, the cooling water flowing into the valve body storage chambers 24, 25 from the first ports 24b, 25b flows into the longitudinal grooves 30f, 31f of the valve bodies 30, 31 → cam grooves 30g, 31g → Even if the guide grooves 30h and 31h are guided to the upper surface side of the spring receiving plates 36 and 37 via the pressure adjusting passages formed by the notches 36a and 37a of the spring receiving plates 36 and 37 and then closed, Will be enclosed. The pressure receiving area on the upper surface side of the spring receiving plates 36 and 37 on which the enclosed cooling water acts is sufficiently larger than the pressure receiving area on the lower end surfaces of the small diameter portions 30a and 31a (bottom plate portions 30c and 31c) of the valve bodies 30 and 31. Because of this relationship, a force that pushes down the valve bodies 30 and 31 downward is caused according to the difference in pressure receiving area.

The flow control device 3 according to the present embodiment has the above-described configuration, and the main action and the effect produced by the flow control device 3 will be described next.
When starting the engine 1 at a low temperature, the engine 1 must be warmed as soon as possible. During such warm-up operation, the cooling water is not circulated through the cooling circuit 8, but the first cooling water passage 1a passing through the water jacket on the cylinder head side and the second cooling passing through the water jacket on the cylinder block side. It is important to retain the water in the two cooling water passages with the water passage 1b.
At this time, the command device 14 does not drive the motor 13, the valves 10 and 11 of the valve mechanism 12 are in the initial setting state, and the first passages 10a and 11a are closed.
That is, in each valve 10 and 11, the bottom plate portions 30c and 31c of the valve bodies 30 and 31 are seated on the bottom portions 24a and 25a of the valve body storage chambers 24 and 25, and the first port 24c leading to the first passages 10a and 11a. , 25c are closed (the poppet valve portion P constituting the first flow rate control portion is in a closed state).

Thus, when the first passages 10a and 11a are blocked, the water pump 2 is driven by the engine 1 and the cooling water in the first cooling water passage 1a and the second cooling water passage 1b may become high pressure. Therefore, high water tightness is required for the valve closing function of the poppet valve portion P that constitutes the first flow rate control portion.
In response to such a requirement, each poppet valve portion P is configured to sufficiently satisfy the high water tightness as follows.
First, the valve bodies 30 and 31 are configured so that the lower end surfaces of the bottom plate portions 30c and 31 receive an axial downward pressing force by the springs 40 and 41, and the tops of the bottom portions 24a and 25a of the valve body storage chambers 24 and 25 are detected. Press contact with the end face.
Second, since the pressure receiving area on the upper surface side of the spring receiving plates 36 and 37 is larger than the pressure receiving area on the lower end surfaces of the small diameter portions 30a and 31a of the valve bodies 30 and 31, it corresponds to the difference in pressure receiving area. The cooling water pressure is added to the pressing force, and the pressure contact force is further increased.
Therefore, the poppet valve portion P can obtain a sufficient watertight function despite the watertight structure by the face seal, and can achieve a completely closed state of the first passages 10a and 11a.
Thereby, at the time of warming-up of the engine 1 that keeps the cooling water passages 1a and 1b in the shut-off state, the leakage flow rate of the cooling water can be minimized, the warm-up time of the engine 1 can be shortened, and the temperature of the main body of the engine 1 can be reduced. Can be maintained high, so that efficient operation is possible.

  Further, as described above, by securing a sufficient seal at the poppet valve portion P, it is not necessary to strictly seal the rotary valve portion R arranged in series, and a clearance seal is sufficient. Thus, there is no increase in driving resistance due to the sealing mechanism of the rotary valve, and the valve bodies 30, 31 can be rotationally driven by a driving source (motor 13) with a small driving torque. Thus, the size of the flow control device as a whole can be reduced by downsizing the drive source, and it can be sufficiently mounted in a narrow space around the engine.

  Further, the method (mechanism) for securing the valve closing position of the poppet valve portion P is characterized. That is, in the direction changing means for converting the valve bodies 30, 31 from the rotational direction displacement to the axial direction displacement, when the poppet valve portion P is in the closed position, the pin members 32, 33 are changed from the cam grooves 30g, 31g to the guide grooves 30h, It moves to 31h and the restraint of the axial direction of the pin members 32 and 33 is cancelled | released. Accordingly, the valve bodies 30 and 31 can freely move in the axial direction, are pushed down by the urging force of the springs 40 and 41, and are seated on the bottom portions 24a and 25a of the valve body storage chambers 24 and 25. Thus, the valve closing position of the poppet valve portion P is automatically determined with high accuracy.

  Therefore, if the rotational displacement of the motor 13 is simply converted into the axial displacement (restricted in the axial direction) as in the conventional poppet valve, the axial positions of the valve bodies 30 and 31 are the same as those of the motor 13. In relation to the rotational position, a desired valve closing function cannot be obtained unless the rotational stop position of the motor 13 is accurately determined. In contrast, this embodiment provides such a precise rotational stop positioning function. Is not required. The advantage is that, in particular, when a plurality of valves 10 and 11 are driven by a single drive source (motor 13) as in the present embodiment, it is not necessary to strictly manage variations in the respective rotation angles. Demonstrate.

On the other hand, after the warm-up of the engine 1 is finished, the cooling circuit 8 is used to make the temperature of the engine 1 appropriate.
The motor 13 is energized and controlled by the command device 14 in accordance with the operating state of the engine 1. The valves 10 and 11 of the valve mechanism 12 are released from the initial setting state. First, after the poppet valve portion P that forms the first flow control section opens the first passages 10a and 11a, the rotary that forms the second flow control section. The valve portion R opens the second passages 10b and 11b and the third passages 10c and 11c.
That is, when the valve bodies 30, 31 are rotated by being driven by the motor 13, in the initial stage of the rotation, the pin members 32, 33 and the cam grooves 30g, 31g are engaged with the springs 40, 41 according to the cam profile. Ascends in the axial direction. Due to the axial displacement of the valve bodies 30, 31, the bottom plate parts 30 c, 31 c of the small diameter parts 30 a, 31 a are separated from the bottom parts 24 a, 25 a of the valve body storage chambers 24, 25, leading to the first passages 10 a, 11 a. 1 port 24b, 25b is opened (the poppet valve part P which makes the 1st flow control part opens). At this time, the large-diameter portions 30b and 31b of the valve bodies 30 and 31 maintain a state in which the second ports 24c and 25c and the third ports 24d and 25d are closed (the rotary valve forming the second flow control unit). Part R is in a closed state).
Then, when further rotated, the large diameter portions 30b and 31b of the valve bodies 30 and 31 open the second ports 24c and 25c and the third ports 24d and 25d (the rotary valve portion R opens).
Thus, the cooling water is divided into the radiator passage 4 and the bypass passage 7 and adjusted to an appropriate temperature.

[Modification]
As mentioned above, although Example 1 was explained in full detail, the concrete structure and arrangement position of the flow control device 3 can be variously changed without departing from the spirit of the present invention. This is illustrated in
(1) A linear solenoid is used in place of the motor 13 as a drive source, and the valve bodies 30 and 31 are driven in the axial direction. The movement in the axial direction is converted into the rotational direction by the direction changing means, and the valve bodies 30 and 31 are driven. May be rotationally displaced. Such a direction changing means can be easily realized by making the cam profiles of the cam grooves 30g, 31g with which the pin members 32, 33 are engaged into, for example, vertical grooves that are inclined in the axial direction.
(2) The third ports 24d and 25d may be directly communicated with each other in the valve main body 21 so that the connection pipes 28 and 29 of the valve main body 21 are made common.
(3) A part of the cam grooves 30g and 31g (including the guide grooves 30h and 31h) is also used as the pressure adjusting passage to further reduce the structure. For example, the large-diameter portion 30b of the valve bodies 30 and 31 is used. , 31b may be provided with longitudinal grooves directly communicating with the notches 36a, 37a of the spring receiving plates 36, 37 to form independent pressure adjusting passages.
(4) In the present embodiment, the same amount of cooling water is diverted to the radiator passage 4 and the bypass passage 7, but the configuration of each rotary valve portion R is changed, for example, the size of the valve bodies 30 and 31 is large. In the diameter portions 30b and 31b, the size and arrangement of the window portions 30e and 31e are variously changed so that the flow passes through only one of the radiator passage 4 and the bypass passage 7 and then is divided into the other as necessary. Various adjustments such as varying the partial flow rate of 7 are possible.
(5) In this embodiment, the present invention is applied to the case where the cooling circuit 8 of the engine 1 has two cooling water passages 1a and 1b, but when the cooling water passage of the engine 1 has only one system, the valve 10 or 11 may be configured using only one of them.

  In the above-described embodiment, the application example to the cooling device using the engine 1 as a prime mover has been described in detail. However, even in the case of a drive motor in another prime mover, for example, an electric vehicle, a cooling circuit for this drive motor. Of course, the flow control device of the present invention can be applied in the same manner.

1 engine (motor)
3 Flow control device 8 Cooling circuit 10, 11 Valve 10a, 11a First passage (first port)
10b, 11b Second passage (second port)
10c, 11c Third passage (second port)
12 Valve mechanism 13 Motor (drive source)
20 housing 21 valve body 22 middle lid 23 outer lid 24 first valve body storage chamber 25 second valve body storage chamber 24a, 25a bottom (receiving surface)
24b, 25b 1st port (a part of 1st flow control part)
24c, 25c 2nd port (a part of 2nd flow control part)
24d, 25d 3rd port (part of 2nd flow control part)
30 1st valve body 31 2nd valve body 30b, 31b Large diameter part (a part of 2nd flow control part)
30c, 31c Bottom plate part (a part of the first flow control part, one end face in the axial direction)
30d, 31d Window (first opening)
30e, 31e Window (second opening)
30f, 31f Vertical groove (pressure adjustment passage)
30g, 31g Cam groove (direction changing means, pressure adjusting passage)
30h, 31h Guide groove (direction changing means, pressure adjusting passage)
32, 33 Pin member (direction changing means)
36, 37 Spring receiving plate 36a, 37a Notch (pressure adjusting passage)
40, 41 Spring (biasing means)
P Poppet valve part (first flow control part)
R Rotary valve part (second flow rate control part)

Claims (10)

In a flow control device that is disposed in a cooling circuit of a prime mover and controls the flow rate of a cooling medium that circulates through the cooling circuit,
(A) a housing that is connected to the cooling circuit and has a first port and a second port that input and output the cooling medium, and a valve body storage chamber that communicates between the first and second ports;
(B) a valve body that is housed in the valve body housing chamber so as to be capable of axial displacement and rotational displacement, and that connects and disconnects the ports;
(C) a drive source for driving the valve body in one of the axial direction and the rotational direction;
(D) direction changing means for displacing the valve body in either the axial direction or the rotation direction by driving the valve body in one direction by the drive source;
(E) a first flow rate control unit configured by one end surface of the valve body in the axial direction and the first port;
(F) a second flow rate control unit configured by a circumferential surface of the valve body in the circumferential direction and the second port;
With
The flow rate control device characterized in that the first flow rate control unit is controlled to open and close by the axial displacement of the valve body, and the second flow rate control unit is controlled to open and close by the rotational direction displacement of the valve body. In a flow control device that is disposed in a cooling circuit of a prime mover and controls the flow rate of a cooling medium that circulates through the cooling circuit,
(A) a housing that is connected to the cooling circuit and has a first port and a second port that input and output the cooling medium, and a valve body storage chamber that communicates between the first and second ports;
(B) a valve body that is housed in the valve body housing chamber so as to be capable of axial displacement and rotational displacement, and that connects and disconnects the first and second ports;
(C) a drive source for driving the valve body in the rotational direction;
(D) direction changing means for axially displacing the valve body in accordance with displacement in the rotational direction of the valve body;
(E) a first flow rate control unit configured by one end surface of the valve body in the axial direction and the first port;
(F) a second flow rate control unit configured by a circumferential surface of the valve body in the circumferential direction and the second port;
With
The flow rate control device characterized in that the first flow rate control unit is controlled to open and close by the axial displacement of the valve body, and the second flow rate control unit is controlled to open and close by the rotational direction displacement of the valve body. In the flow control device according to claim 1 or 2,
When the valve body is driven by the driving source, the second flow rate control unit is opened after the first flow rate control unit is opened. In the flow control device according to claim 1 or 2,
In the first flow rate control unit, a face seal is formed by one end surface of the valve body and a receiving surface of the valve body storage chamber with which the one end surface abuts in the axial direction.
The second flow rate control unit is characterized in that a clearance seal is formed by a gap between a peripheral surface of the valve body and a peripheral surface of the valve body storage chamber with which the peripheral surface is in sliding contact. Control device. In the flow control device according to any one of claims 1 to 4,
The valve body communicates with each other inside thereof, and has a first opening and a second opening that respectively open on the peripheral surface side of the valve body,
The first opening communicates with the first port when the valve element is axially displaced to a valve opening position;
The flow rate control device, wherein the second opening communicates with the second port when the valve body is displaced in the rotational direction by a predetermined amount. In the flow control device according to any one of claims 1 to 5,
The flow rate control device, wherein the direction changing means includes a pin member and a cam groove which are provided in the valve body storage chamber and the valve body and engage with each other. The flow control device according to claim 6,
The valve body storage chamber is provided with a biasing means for biasing the valve body toward one end surface side.
The flow rate control device characterized in that the direction changing means releases the axial restriction between the pin member and the cam groove when the valve body is in a valve closing position of the first flow rate control unit. In the flow control device according to any one of claims 1 to 7,
The first port is connected to a cooling medium supply side of the cooling circuit;
A flow rate control device, characterized in that a pressure adjusting passage is provided for communicating one end surface side and the other end surface side of the valve body. The flow control device according to claim 8, wherein
The valve body has a pressure receiving area on the one end face side set to be smaller than a pressure receiving area on the other end face side. In the flow control device according to claim 8 or 9,
The cam groove also serves as a part of the pressure adjustment passage.

Images