CN105190136A - Rotary valve device - Google Patents

Rotary valve device Download PDF

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Publication number
CN105190136A
CN105190136A CN201380074846.3A CN201380074846A CN105190136A CN 105190136 A CN105190136 A CN 105190136A CN 201380074846 A CN201380074846 A CN 201380074846A CN 105190136 A CN105190136 A CN 105190136A
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China
Prior art keywords
mentioned
valve
valve member
hydrodynamic pressure
chamber
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Granted
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CN201380074846.3A
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Chinese (zh)
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CN105190136B (en
Inventor
高田裕正
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Saginomiya Seisakusho Inc
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Saginomiya Seisakusho Inc
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
    • F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
    • F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
    • F16K11/072—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members
    • F16K11/074—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces
    • F16K11/0743—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with pivoted closure members with flat sealing faces with both the supply and the discharge passages being on one side of the closure plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K3/00—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing
    • F16K3/02—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor
    • F16K3/04—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members
    • F16K3/10—Gate valves or sliding valves, i.e. cut-off apparatus with closing members having a sliding movement along the seat for opening and closing with flat sealing faces; Packings therefor with pivoted closure members with special arrangements for separating the sealing faces or for pressing them together
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K39/00—Devices for relieving the pressure on the sealing faces
    • F16K39/04—Devices for relieving the pressure on the sealing faces for sliding valves
    • F16K39/045—Devices for relieving the pressure on the sealing faces for sliding valves of rotating or pivoting type

Abstract

Provided is a rotary valve device that can suppress the force for pressing a valve member against a valve seat surface. In a two-way valve (1), the cylindrical section (31) of a valve member (30) has a small-diameter cylindrical portion (31a), a large-diameter cylindrical portion (31b), and a cylindrical portion step surface (31c) formed between the outer peripheral surface (31a1) of the small-diameter cylindrical portion (31a) and the outer peripheral surface (31b1) of the large-diameter cylindrical portion (31b). Also, a valve main body (10) has a valve member support section (15) provided with: a small-diameter hole section (15a) to which the small-diameter cylindrical portion (31a) can rotatably fit; a large-diameter hole section (15b) to which the large-diameter cylindrical portion (31b) can rotatably fit; and a support section step surface (15c) formed between the inner peripheral surface (15a1) of the small-diameter hole section (15a) and the inner peripheral surface (15b1) of the large-diameter hole section (15b). Also, an annular seal ring (38) is provided in the seal space (R) encircled by the outer peripheral surface (31a1) of the small-diameter cylindrical portion, the cylindrical portion step surface (31c), the inner peripheral surface (15b1) of the valve large-diameter hole section, and the support section step surface (15c).

Description

Rotary valve device
Technical field
The present invention relates to the rotary valve device of the connected relation being switched the multiple valve ports determined accordingly with the stop position of this valve member by the rotation of valve member.
Background technique
As rotary valve device in the past, such as, four-way switching valve disclosed in patent documentation 1 has as illustrated in fig. 18: the valve chest 811 of large footpath cylindrical shape; Be connected with the upper end side of valve chest 811 one and the motor casing 812 of the blocked path cylindrical shape in upper end; To carry out to the other end side opening of valve chest 811 the flat valve seat 813 that airtight mode is installed on this valve chest 811; With valve seat 813 towards the stacked revolving spool 814 of the valve seat surface 813a inside valve chest 811; In the drawings above-below direction divides the space in valve chest 811 and the spacing wall 807 of mineralization pressure balance cylinder 808 and valve chamber 809; Be built in the planet-gear speed reducer 815 of the pressure equalizing chamber 808 in valve chest 811; And stepper motor 820.
The the first fixing port E1 be provided with the first switching port C1 (not shown) and the second switching port C2 at valve seat 813, being reversibly communicated with these switching ports C1, C2 and the second fixing port E2.Spool 814 is contained in valve chest 811, and its cylindrical portion 814a can be supported on the through hole 807a arranged in the central authorities of spacing wall 807 rotatably, the skirt section 814b be connected with cylindrical portion 814a one and valve seat surface 813a overlapping configuration.At this skirt section 814b, be provided with the air tight communication hole 814c be always communicated with the second fixing port E2.Spool 814 is connected with the output shaft 815a of planet-gear speed reducer 815, rotates along with the rotation of output shaft 815a.
This four-way switching valve 801 transmits the rotation of stepper motor 820 to spool 814 via planet-gear speed reducer 815, and spool 814 rotates to switch to stop position.Thus, when spool 814 is in a stop position, connect the second fixing port E2 and the second switching port C2 by air tight communication hole 814c in the mode be communicated with, and make the first fixing port E1 expose at valve chamber 809 with the first switching port C1 and be connected these mouths in the mode be communicated with.And, when spool 814 is in other stop position, connect the second fixing port E2 and the first switching port C1 by air tight communication hole 814c in the mode be communicated with, and make the first fixing port E1 expose at valve chamber 809 with the second switching port C2 and be connected these mouths in the mode be communicated with.Like this, the connected relation of each mouth is switched.
Such four-way switching valve 801 such as loads refrigerant circulation loop that refrigeration agent is circulated between the indoor set and outdoor unit of air-conditioning etc. and uses.In this case, the second fixing port E2 of four-way switching valve 801 is connected with the suction side of compressor.Therefore, the flow direction of the second fixing port E2 streaming flow is constant and hydrodynamic pressure is also smaller, thus the pressure (hydrodynamic pressure) of refrigeration agent in the 814c of air tight communication hole and in pressure equalizing chamber 808 can not change and somewhat constant significantly.
On the other hand, such rotary valve device such as also in the loop that the flow direction of fluid changes etc. in use.As the structure of the Twoway valves of an example of the rotary valve device used in the loop that the flow direction at fluid changes etc. as shown in Figure 19, Figure 20.
Twoway valves 901 shown in Figure 19 possesses valve body 910 and is contained in the valve member 930 in valve body 910.Valve member 930 possess can around axis rotation be supported on valve body 910 cylindrical portion 931 and the spool portion 933 of skirt shape that is connected with cylindrical portion 931 one.Valve member 930 is contained in valve body 910, is valve chamber B and back pressure chamber H thus by the spatial division in valve body 910.Further, between cylindrical portion 931 and valve body 910, be provided with sealed member 938, utilize sealing parts 938, come mutually to separate valve chamber B and back pressure chamber H hermetically.Applied the power pushed to the seat portion 920 being integrally provided on valve body 910 by helical spring 963 pairs of valve members 930, the lower end surface 933a in this spool portion 933 is connected to the valve seat surface 922a of seat portion 920.Be formed with the airtight recess 934 expanded to spool portion 933 at the lower end surface 933a in spool portion 933, between this airtight recess 934 and valve seat surface 922a, be formed with confined space G.Further, at valve member 930, the confined space G of connecting valve core 933 and the balancing orifice 936 of back pressure chamber H is formed.
In seat portion 920, be formed at the first valve port P1 of valve seat surface 922a opening and the second valve port P2.And valve member 930 is rotated by rotary driving part 950 via rotary shaft 940, carrys out at least one party in opening and closing first valve port P1 and the second valve port P2.Specifically, as shown in Figure 20 (a), first valve port P1 and the second valve port P2 all exposes at valve chamber B and allows the flowing (valve opening state) of fluid, or as shown in Figure 20 (b), Figure 20 (c), (namely either party of first valve port P1 and the second valve port P2 covered by the spool portion 933 of valve member 930, expose in confined space G), and the flowing of fluid is restricted (valve closing state).
And, such as, when either party of the first valve port P1 and the second valve port P2 is covered by the spool portion 933 of valve member 930 and the flowing of fluid is restricted, if the flow direction change of fluid, in hydrodynamic pressure then in valve chamber B and confined space G and in back pressure chamber H (namely, the side covered by spool portion 933 in first valve port P1 and the second valve port P2) hydrodynamic pressure between relationship change, and according to circumstances different, because hydrodynamic pressure acts on the power making it to float from seat portion 920 relative to valve member 930.
Therefore, power valve member 930 being pushed on seat portion 920 of setting helical spring 963, even if when relationship change between the hydrodynamic pressure in the hydrodynamic pressure in valve chamber B and confined space G and in back pressure chamber H, also can not float from seat portion 920.
Prior art document
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Publication 2001-141093 publication
Summary of the invention
Invent problem to be solved
In above-mentioned Twoway valves 901, such as, because of the various essential factor such as figure tolerance of valve member 930, the equilibrium of forces that the hydrodynamic pressure putting on valve member 930 produces changes.Therefore, the power of this valve member 930 of pushing that setting helical spring 963 produces, even if so that when most assignment example, valve member 930 also can not float from seat portion 920.
Below, about the setting of helical spring 963, with reference to Figure 21 ~ Figure 26, concrete example is described.
Such as, as shown in Figure 21 (a), when valve member 930 is pushed on seat portion 920 by helical spring 963, think because of figure tolerance, the outer periphery 933a1 of the lower end surface 933a in spool portion 933 can be connected to valve seat surface 922a, and inner circumference edge 933a2 can leave from valve seat surface 922a.In this case, the lower end surface 933a in spool portion 933 is applied to the hydrodynamic pressure in confined space G.That is, as shown in Figure 21 (b), the area S1 that overlooks being subject to the position of the hydrodynamic pressure in confined space G in valve member 930 becomes area (oblique line portion) in the outer periphery 933a1 of the lower end surface 933a in spool portion 933.Below, this structure is called " confined space max structure ".
And, as shown in Figure 22 (a), when valve member 930 is pushed on seat portion 920 by helical spring 963, think because of figure tolerance, the inner circumference edge 933a2 of the lower end surface 933a in spool portion 933 can be connected to valve seat surface 922a, and outer periphery 933a1 can leave from valve seat surface 922a.In this case, the lower end surface 933a in spool portion 933 is applied to the hydrodynamic pressure in valve chamber B.That is, as shown in Figure 22 (b), the area S2 that overlooks being subject to the position of the hydrodynamic pressure in confined space G in valve member 930 becomes area (oblique line portion) in the inner circumference edge 933a2 of the lower end surface 933a in spool portion 933.Below, this structure is called " confined space minimal structure ".
And, the situation higher than the hydrodynamic pressure in valve chamber B for the hydrodynamic pressure respectively in above-mentioned confined space max structure and confined space minimal structure, in confined space G and in back pressure chamber H and these four examples of low situation, below represent an example to the power that valve member 930 acts on.
In the following description, (namely the area SH that overlooks of the upper-end surface 931a of the cylindrical portion 931 of valve member 930 is set to 380 square millimeters, the diameter D of cylindrical portion 931 is set to 22mm), above-mentioned during confined space max structure is overlooked area S1 (, area in the outer periphery 933a1 of lower end surface 933a) be set to 385 square millimeters, above-mentioned during confined space minimal structure is overlooked area S2 (that is, the area in the inner circumference edge 933a2 of lower end surface 933a) and be set to 250 square millimeters.
And, the pressure difference Δ P1 of the above-mentioned hydrodynamic pressure when hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B is set to 3.0MPa, and the pressure difference Δ P2 of the above-mentioned hydrodynamic pressure when hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B is set to-3.0MPa.
The power F1 acted on valve member 930 by the hydrodynamic pressure in confined space G is obtained by the area (above-mentioned overlook area S1 or S2) of overlooking being subject to the position of the hydrodynamic pressure in the confined space G pressure difference (above-mentioned pressure difference Δ P1 or Δ P2) between the hydrodynamic pressure in the hydrodynamic pressure in confined space G and valve chamber B be multiplied by valve member 930.The power F2 acted on valve member 930 by the hydrodynamic pressure in back pressure chamber H is obtained by the area (above-mentioned overlook area SH) of overlooking being subject to the position of the hydrodynamic pressure in the back pressure chamber H pressure difference (above-mentioned pressure difference Δ P1 or Δ P2) between the hydrodynamic pressure in the hydrodynamic pressure in back pressure chamber H and valve chamber B be multiplied by valve member 930.Further, below by towards valve seat surface pushing valve member 930 towards being just set to.
(example 1: in confined space max structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B)
In the example 1 shown in Figure 23, by the hydrodynamic pressure in confined space G, the power F1 that valve member 930 acts on is become:
F1＝(－ΔP1)×S1＝－1155[N]…(1－1)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 930 acts on is become:
F2＝ΔP1×SH＝1140[N]…(1－2)。
Therefore, by above-mentioned formula, following power is acted on to valve member 930:
F＝F1+F2＝－15[N]，
That is, to make valve member 930 have the power of 15 [N] from the mode effect that valve seat surface 922a floats.In this case, need to utilize helical spring 963 so that at least the power of [N] pushes valve member 930 towards valve seat surface 922a more than 15.
(example 2: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B)
In the example 2 shown in Figure 24, by the hydrodynamic pressure in confined space G, the power F1 that valve member 930 acts on is become:
F1＝(－ΔP1)×S2＝－750[N]…(1－3)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 930 acts on is become:
F2＝ΔP1×SH＝1140[N]…(1－4)。
Therefore, by above-mentioned formula, following power is acted on to valve member 930:
F＝F1+F2＝390[N]，
That is, the power of 390 [N] is had with mode effect valve member 930 being pushed on valve seat surface 922a.In this case, even if do not utilize helical spring 963 to push valve member 930 towards valve seat surface 922a, valve member 930 also can not float from valve seat surface 922a.
(example 3: in confined space max structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B)
In the example 3 shown in Figure 25, by the hydrodynamic pressure in confined space G, the power F1 that valve member 930 acts on is become:
F1＝(－ΔP2)×S1＝1155[N]…(1－5)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 930 acts on is become:
F2＝ΔP2×SH＝－1140[N]…(1－6)。
Therefore, by above-mentioned formula, following power is acted on to valve member 930:
F＝F1+F2＝15[N]，
That is, the power of 15 [N] is had with mode effect valve member 930 being pushed on valve seat surface 922a.In this case, even if do not utilize helical spring 963 to push valve member 930 towards valve seat surface 922a, valve member 930 also can not float from valve seat surface 922a.
(example 4: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B)
In the example 4 shown in Figure 26, by the hydrodynamic pressure in confined space G, the power F1 that valve member 930 acts on is become:
F1＝(－ΔP2)×S2＝750[N]…(1－7)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 930 acts on is become:
F2＝ΔP2×SH＝－1140[N]…(1－8)。
Therefore, by above-mentioned formula, following power is acted on to valve member 930:
F＝F1+F2＝－390[N]，
That is, to make valve member 930 have the power of 390 [N] from the mode effect that valve seat surface 922a floats.In this case, need to utilize helical spring 963 so that at least the power of [N] pushes valve member 930 towards valve seat surface 922a more than 390.
In above-mentioned example 1 ~ 4, in the example 4 of the situation that the hydrodynamic pressure especially in back pressure chamber is lower than the hydrodynamic pressure in valve chamber, valve member 930 becomes maximum from the power that valve seat surface 922a floats.Therefore, in order to situation valve member 930 arbitrary in example 1 ~ 4 all can not float from valve seat surface 922a, and in the example 4 as most assignment example, valve member 930 can not be floated from valve seat surface 922a.That is, the power FS towards valve seat surface 922a pushing valve member 930 that helical spring 963 produces is set as at least exceeding the power that is 390 [N] that in example 4, valve member 930 are floated.
But, in above-mentioned Twoway valves 901, the power FS towards valve seat surface 922a pushing valve member 930 produced by helical spring 963 when supposing above-mentioned example 4 is such as set to 391 [N], if become the state of above-mentioned example 2, then relative to valve member 930, all apply the power F (=390 [N]) being pushed on valve seat surface 922a by hydrodynamic pressure and the power FS (=391 [N]) utilizing helical spring 963 to push towards valve seat surface 922a, and with stronger power, valve member 930 is pushed on valve seat surface 922a.Therefore, drive the valve member 930 be pushed with so stronger power to make it to rotate and need larger power, thus exist and have to make rotary driving part 950 to maximize this problem.
Therefore, problem of the present invention is to provide the rotary valve device that can suppress power valve member being pushed on valve seat surface.
For solving the scheme of problem
In order to solve above-mentioned problem, the invention described in scheme 1 is a kind of rotary valve device, possesses: valve body, and it is provided with space in inner side, seat portion, it has the plane valve seat surface towards above-mentioned space and two valve ports at this valve seat surface opening, valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, by rotating the connected relation switching above-mentioned two valve ports determined accordingly with stop position, and pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface, and the feature of above-mentioned rotary valve device is, above-mentioned valve member has: axle portion, and it can be supported on above-mentioned valve body rotatably around axle center, and spool portion, it is located at the one end in above-mentioned axle portion, and with at least one valve port in above-mentioned two valve ports of above-mentioned stop position opening and closing accordingly, above-mentioned valve body is by dividing above-mentioned space by above-mentioned valve member, thus there is the end side that is formed at above-mentioned axle portion and hold the valve chamber in above-mentioned spool portion, with the back pressure chamber of another side being formed at above-mentioned axle portion, above-mentioned valve body or above-mentioned valve member have connect in above-mentioned two valve ports by the valve port of above-mentioned spool portion opening and closing and the Jun Ya road of above-mentioned back pressure chamber, be configured to, in above-mentioned valve member when the hydrodynamic pressure of above-mentioned back pressure chamber is lower than the hydrodynamic pressure of above-mentioned valve chamber be subject to the hydrodynamic pressure of above-mentioned back pressure chamber overlook area, it is little that above-mentioned during the hydrodynamic pressure height of the hydrodynamic pressure comparing above-mentioned back pressure chamber than above-mentioned valve chamber overlooks area.
In order to solve above-mentioned problem, the invention described in scheme 2 is a kind of rotary valve device, possesses: valve body, and it is provided with space in inner side, seat portion, it has the plane valve seat surface towards above-mentioned space and the multiple valve ports at this valve seat surface opening, valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, and by rotating the connected relation switching the above-mentioned multiple valve port determined accordingly with stop position, and pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface, and the feature of above-mentioned rotary valve device is, above-mentioned valve member has: axle portion, and it can be supported on above-mentioned valve body rotatably around axle center, and spool portion, it is located at the one end in above-mentioned axle portion, and be provided with one or more airtight access, this one or more airtight access forms confined space between above-mentioned valve seat surface, and be communicated with above-mentioned multiple valve port that regulation combines accordingly with above-mentioned stop position by this confined space, above-mentioned valve body is by dividing above-mentioned space by above-mentioned valve member, thus there is the end side that is formed at above-mentioned axle portion and hold the valve chamber in above-mentioned spool portion, with the back pressure chamber of another side being formed at above-mentioned axle portion, above-mentioned valve body or above-mentioned valve member have the Jun Ya road of any one and the above-mentioned back pressure chamber connected in above-mentioned airtight access, be configured to, in above-mentioned valve member when the hydrodynamic pressure of above-mentioned back pressure chamber is lower than the hydrodynamic pressure of above-mentioned valve chamber be subject to the hydrodynamic pressure of above-mentioned back pressure chamber overlook area, it is little that above-mentioned during the hydrodynamic pressure height of the hydrodynamic pressure comparing above-mentioned back pressure chamber than above-mentioned valve chamber overlooks area.
The invention of invention described in scheme 3 described in scheme 1 or 2, it is characterized in that, between above-mentioned valve body and above-mentioned valve member, be provided with the sealed member to the ring-type sealed between them, and be configured to, when hydrodynamic pressure height than above-mentioned valve chamber of the hydrodynamic pressure of above-mentioned back pressure chamber, above-mentioned sealed member is pushed on above-mentioned valve member, and above-mentioned sealed member is pushed on above-mentioned valve body when the hydrodynamic pressure of above-mentioned back pressure chamber is lower than the hydrodynamic pressure of above-mentioned valve chamber.
The invention of invention described in scheme 4 described in scheme 3, is characterized in that, the above-mentioned axle portion of above-mentioned valve member has: path shaft portion, and it configures in the mode of an end face towards above-mentioned back pressure chamber; Large journal axle part, it is connected coaxially with the other end of this path shaft portion; And axle portion step surface, it is formed between the outer circumferential face of above-mentioned path shaft portion and the outer circumferential face of above-mentioned large journal axle part, above-mentioned valve body has valve member support, and this valve member support is provided with: diameter holes portion, and above-mentioned path shaft portion is fitting for rotating by it; Hole portion, large footpath, above-mentioned large journal axle part is fitting for rotating by it; And support step surface, it is formed between the inner peripheral surface in above-mentioned diameter holes portion and the inner peripheral surface in large hole, footpath portion, above-mentioned sealed member is arranged in the space that impaled by the inner peripheral surface in the outer circumferential face of above-mentioned path shaft portion, above-mentioned axle portion step surface, hole portion, above-mentioned large footpath and above-mentioned support step surface, to seal between the outer circumferential face of above-mentioned path shaft portion and the inner peripheral surface in hole portion, above-mentioned large footpath.
In order to solve above-mentioned problem, the invention described in scheme 5 is a kind of rotary valve device, possesses: valve body, and it is provided with space in inner side, seat portion, it has the plane valve seat surface towards above-mentioned space and two valve ports at this valve seat surface opening, valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, and by rotating the connected relation switching above-mentioned two valve ports determined accordingly with stop position, and pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface, and the feature of above-mentioned rotary valve device is, above-mentioned valve member has: cylindrical portion, and it can be supported on above-mentioned valve body rotatably around axle center, and spool portion, it is connected with one end of above-mentioned cylindrical portion, and with at least one valve port in above-mentioned two valve ports of above-mentioned stop position opening and closing accordingly, above-mentioned valve body is by dividing above-mentioned space by above-mentioned valve member, thus there is the end side that is formed at above-mentioned cylindrical portion and hold the valve chamber in above-mentioned spool portion, with the back pressure chamber of another side being formed at above-mentioned cylindrical portion, above-mentioned valve body or above-mentioned valve member have connect in above-mentioned two valve ports by the valve port of above-mentioned spool portion opening and closing and the Jun Ya road of above-mentioned back pressure chamber, above-mentioned cylindrical portion has: path column part, it configures in the mode of an end face towards above-mentioned back pressure chamber, large footpath column part, it is connected coaxially with the other end of this path column part, and cylindrical portion step surface, it is formed between the outer circumferential face of above-mentioned path column part and the outer circumferential face of above-mentioned large footpath column part, above-mentioned valve body has valve member support, and this valve member support is provided with: diameter holes portion, and above-mentioned path column part is fitting for rotating by it, hole portion, large footpath, above-mentioned large footpath column part is fitting for rotating by it, and support step surface, it is formed between the inner peripheral surface in above-mentioned diameter holes portion and the inner peripheral surface in large hole, footpath portion, in the space that inner peripheral surface and the above-mentioned support step surface by the outer circumferential face of above-mentioned path column part, above-mentioned cylindrical portion step surface, hole portion, above-mentioned large footpath impales, be provided with the sealed member to the ring-type sealed between the outer circumferential face of above-mentioned path column part and the inner peripheral surface in hole portion, above-mentioned large footpath.
In order to solve above-mentioned problem, the invention described in scheme 6 is a kind of rotary valve device, possesses: valve body, and it is provided with space in inner side, seat portion, it has the plane valve seat surface towards above-mentioned space and the multiple valve ports at this valve seat surface opening, valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, by rotating the connected relation switching the above-mentioned multiple valve port determined accordingly with stop position, and pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface, and the feature of above-mentioned rotary valve device is, above-mentioned valve member has: cylindrical portion, and it can be supported on above-mentioned valve body rotatably around axle center, and spool portion, it is connected with one end of above-mentioned cylindrical portion, and be provided with one or more airtight access, this one or more airtight access forms confined space between above-mentioned valve seat surface, and be communicated with above-mentioned multiple valve port that regulation combines accordingly with above-mentioned stop position by this confined space, above-mentioned valve body is by dividing above-mentioned space by above-mentioned valve member, thus there is the end side that is formed at above-mentioned cylindrical portion and hold the valve chamber in above-mentioned spool portion, with the back pressure chamber of another side being formed at above-mentioned cylindrical portion, above-mentioned valve body or above-mentioned valve member have the Jun Ya road of any one and the above-mentioned back pressure chamber connected in above-mentioned airtight access, above-mentioned cylindrical portion has: path column part, it configures in the mode of an end face towards above-mentioned back pressure chamber, large footpath column part, it is connected coaxially with the other end of this path column part, and cylindrical portion step surface, it is formed between the outer circumferential face of above-mentioned path column part and the outer circumferential face of above-mentioned large footpath column part, above-mentioned valve body has valve member support, and this valve member support is provided with: diameter holes portion, and above-mentioned path column part is fitting for rotating by it, hole portion, large footpath, above-mentioned large footpath column part is fitting for rotating by it, and support step surface, it is formed between the inner peripheral surface in above-mentioned diameter holes portion and the inner peripheral surface in large hole, footpath portion, in the space that inner peripheral surface and the above-mentioned support step surface by the outer circumferential face of above-mentioned path column part, above-mentioned cylindrical portion step surface, hole portion, above-mentioned large footpath impales, be provided with the sealed member to the ring-type sealed between the outer circumferential face of above-mentioned path column part and the inner peripheral surface in hole portion, above-mentioned large footpath.
The effect of invention is as follows.
According to the invention described in scheme 1,2, the area of overlooking being subject to the hydrodynamic pressure of back pressure chamber in valve member when the hydrodynamic pressure of back pressure chamber is lower than the hydrodynamic pressure of valve chamber is configured to, and above-mentioned during the hydrodynamic pressure height of the hydrodynamic pressure comparing back pressure chamber than valve chamber overlooks area and less.Like this, hydrodynamic pressure in back pressure chamber is lower than the hydrodynamic pressure in valve chamber, when making it the power of floating from valve seat surface by the hydrodynamic pressure in back pressure chamber to valve member effect, due to the area being subject to the position of the hydrodynamic pressure in back pressure chamber in valve member (namely, overlook area) diminish, so the power making valve member float from valve seat surface can be reduced.Thereby, it is possible to reduce the power towards valve seat surface pushing valve member that pressing component produces, thus power valve member being pushed on valve seat surface can be suppressed.
According to the invention described in scheme 3, between valve body and valve member, be provided with the sealed member to the ring-type sealed between them.And be configured to, when hydrodynamic pressure height than valve chamber of the hydrodynamic pressure of back pressure chamber, sealed member is pushed on valve member, and sealed member is pushed on valve body when the hydrodynamic pressure of back pressure chamber is lower than the hydrodynamic pressure of valve chamber.Like this, for the sealed member for the ring-type sealed between valve body and valve member, be applied with the hydrodynamic pressure of back pressure chamber in the face of its part, be applied with the hydrodynamic pressure of valve chamber in face a part of in addition.And, if sealed member is pushed on valve member when hydrodynamic pressure height than valve chamber of the hydrodynamic pressure of back pressure chamber, then also put on valve member at the hydrodynamic pressure overlooking the back pressure chamber that area applies in the face of a part for sealed member.Further, if sealed member is pushed on valve body when the hydrodynamic pressure of back pressure chamber is lower than the hydrodynamic pressure of valve chamber, then the hydrodynamic pressure of the valve chamber applied in the face of an other part for sealed member also puts on valve body.That is, in valve member when the hydrodynamic pressure of back pressure chamber is lower than the hydrodynamic pressure of valve chamber be subject to the hydrodynamic pressure of back pressure chamber overlook area (, directly or be indirectly subject to power by sealed member overlook area) be configured to, above-mentioned during the hydrodynamic pressure height of the hydrodynamic pressure comparing back pressure chamber than valve chamber overlooks area and less.Like this, hydrodynamic pressure in back pressure chamber is lower than the hydrodynamic pressure in valve chamber, when making it the power of floating from valve seat surface by the hydrodynamic pressure in back pressure chamber to valve member effect, due to the area being subject to the position of the hydrodynamic pressure in back pressure chamber in valve member (namely, overlook area) diminish, so the power making valve member float from valve seat surface can be reduced.Thereby, it is possible to reduce the power towards valve seat surface pushing valve member that pressing component produces, thus power valve member being pushed on valve seat surface can be suppressed.
According to the invention described in scheme 4, the axle portion of valve member has: the path shaft portion configured towards the mode of back pressure chamber with an end face; The large journal axle part be connected coaxially with the other end of this path shaft portion; And the axle portion step surface be formed between the outer circumferential face of path shaft portion and the outer circumferential face of above-mentioned large journal axle part.Valve body has valve member support, and this valve member support is provided with: path shaft portion is fitting for the diameter holes portion that can rotate; Large journal axle part is fitting for the hole portion, large footpath that can rotate; And the support step surface be formed between the inner peripheral surface in diameter holes portion and the inner peripheral surface in large hole, footpath portion.And sealed member is arranged in the space that impaled by the inner peripheral surface in the outer circumferential face of path shaft portion, axle portion step surface, large hole, footpath portion and support step surface, to seal between the outer circumferential face of path shaft portion and the inner peripheral surface in large hole, footpath portion.Like this, for the sealed member of the ring-type sealed between the outer circumferential face of the path shaft portion for valve member and the inner peripheral surface in the hole portion, large footpath of valve body, be applied with the hydrodynamic pressure of back pressure chamber in the face of its part, be applied with the hydrodynamic pressure of valve chamber in face a part of in addition.And when hydrodynamic pressure height than valve chamber of the hydrodynamic pressure of back pressure chamber, sealed member is pushed on the axle portion step surface of valve member, also puts on valve member at the hydrodynamic pressure overlooking the back pressure chamber that area applies in the face of a part for sealed member.Further, when the hydrodynamic pressure of back pressure chamber is lower than the hydrodynamic pressure of valve chamber, sealed member is pushed on the support step surface of valve body, and the hydrodynamic pressure of the valve chamber applied in the face of an other part for sealed member also puts on valve body.That is, in valve member when the hydrodynamic pressure of back pressure chamber is lower than the hydrodynamic pressure of valve chamber be subject to the hydrodynamic pressure of back pressure chamber overlook area (, directly or be indirectly subject to power by sealed member overlook area) be configured to, above-mentioned during the hydrodynamic pressure height of the hydrodynamic pressure comparing back pressure chamber than valve chamber overlooks area and less.That is, hydrodynamic pressure in back pressure chamber is higher than the hydrodynamic pressure in valve chamber, by the hydrodynamic pressure in back pressure chamber, sealed member is pushed on axle portion step surface, and the hydrodynamic pressure applied in the position in the inner part of the external diameter than large journal axle part in the situation of overlooking in back pressure chamber in valve member.And, hydrodynamic pressure in back pressure chamber is lower than the hydrodynamic pressure in valve chamber, by the hydrodynamic pressure in valve chamber, sealed member is pushed on axle portion step surface, and the hydrodynamic pressure applied in the position in the inner part of the external diameter than path shaft portion in the situation of overlooking in back pressure chamber in valve member.Like this, hydrodynamic pressure in back pressure chamber is lower than the hydrodynamic pressure in valve chamber, when making it the power of floating from valve seat surface by the hydrodynamic pressure in back pressure chamber to valve member effect, due to the area being subject to the position of the hydrodynamic pressure in back pressure chamber in valve member (namely, overlook area) diminish, so the power making valve member float from valve seat surface can be reduced.Thereby, it is possible to reduce the power towards valve seat surface pushing valve member that pressing component produces, thus power valve member being pushed on valve seat surface can be suppressed.
According to the invention described in scheme 5,6, the cylindrical portion that can be supported on valve body around axle center rotatably has: the path column part configured towards the mode of back pressure chamber with an end face; The large footpath column part be connected coaxially with the other end of this path column part; And the cylindrical portion step surface be formed between the outer circumferential face of path column part and the outer circumferential face of large footpath column part.Further, valve body has valve member support, and this valve member support is provided with: the path column part of cylindrical portion is fitting for the diameter holes portion that can rotate; The large footpath column part of cylindrical portion is fitting for the hole portion, large footpath that can rotate; And the support step surface be formed between the inner peripheral surface in diameter holes portion and the inner peripheral surface in large hole, footpath portion.And, in the space that inner peripheral surface in the hole portion, large footpath of the valve member support of the outer circumferential face of the path column part by cylindrical portion, cylindrical portion step surface, valve body and support step surface impale, be provided with the sealed member to the ring-type sealed between the outer circumferential face of path column part and the inner peripheral surface in large hole, footpath portion.Like this, the position of the cylindrical portion step surface side in sealed member is applied with the hydrodynamic pressure in valve chamber, and the position of the support step surface side in sealed member is applied with the hydrodynamic pressure in back pressure chamber.Therefore, hydrodynamic pressure in back pressure chamber is higher than the hydrodynamic pressure in valve chamber, by the hydrodynamic pressure in back pressure chamber, sealed member is pushed on cylindrical portion step surface, and the hydrodynamic pressure applied in the position in the inner part of the external diameter than large footpath column part in the situation of overlooking in back pressure chamber in valve member.And, hydrodynamic pressure in back pressure chamber is lower than the hydrodynamic pressure in valve chamber, by the hydrodynamic pressure in valve chamber, sealed member is pushed on cylindrical portion step surface, and the hydrodynamic pressure applied in the position in the inner part of the external diameter than path column part in the situation of overlooking in back pressure chamber in valve member.That is, hydrodynamic pressure in back pressure chamber is lower than the hydrodynamic pressure in valve chamber, when making it the power of floating from valve seat surface by the hydrodynamic pressure in back pressure chamber to valve member effect, because the area being subject to the position of the hydrodynamic pressure in back pressure chamber in valve member diminishes, so the power making valve member float from valve seat surface can be reduced.Thereby, it is possible to reduce the power towards valve seat surface pushing valve member that pressing component produces, thus power valve member being pushed on valve seat surface can be suppressed.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the Twoway valves of the first mode of execution of the present invention.
Fig. 2 is the amplification view of a part for the Twoway valves being exaggerated Fig. 1.
Fig. 3 is the sectional view of the X-X line along Fig. 1, a () represents that valve member is in the state (valve opening state) of the first stop position, b () represents that valve member is in the state (closing the valve closing state of the first valve port) of the second stop position, (c) represents that valve member is in the state (closing the valve closing state of the second valve port) of the 3rd stop position.
Fig. 4 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming maximum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space max structure) of the valve member possessing (a).
Fig. 5 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming minimum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space minimal structure) of the valve member possessing (a).
Fig. 6 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 1: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
Fig. 7 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 2: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
Fig. 8 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 3: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
Fig. 9 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 4: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
Figure 10 is the longitudinal section of the flow channel switching valve of the second mode of execution of the present invention.
Figure 11 is the sectional view of the X-X line along Figure 10, and (a) represents that valve member is in the state of the first stop position, and (b) represents that valve member is in the state of the second stop position.
Figure 12 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming maximum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space max structure) of the valve member possessing (a).
Figure 13 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming minimum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space minimal structure) of the valve member possessing (a).
Figure 14 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 1: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
Figure 15 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 2: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
Figure 16 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 3: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated Figure 16 (a).
Figure 17 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 4: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
Figure 18 is the longitudinal section of the four-way switching valve of an example of rotary valve device in the past.
Figure 19 is the longitudinal section of the Twoway valves of the another one example of rotary valve device in the past.
Figure 20 is the sectional view of the X-X line along Figure 19, a () represents that valve member is in the state (valve opening state) of the first stop position, b () represents that valve member is in the state (closing the valve closing state of the first valve port) of the second stop position, (c) represents that valve member is in the state (closing the valve closing state of the second valve port) of the 3rd stop position.
Figure 21 is the figure of the position of hydrodynamic pressure in the confined space being subject to spool portion in the valve member of the Twoway valves that Figure 19 is described, a () is the sectional view of the valve member of the confined space in spool portion when becoming maximum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space max structure) of the valve member possessing (a).
Figure 22 is the figure of the position of hydrodynamic pressure in the confined space being subject to spool portion in the valve member of the Twoway valves that Figure 19 is described, a () is the sectional view of the valve member of the confined space in spool portion when becoming minimum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space minimal structure) of the valve member possessing (a).
Figure 23 is the figure of the action of the Twoway valves that Figure 19 is described, a () is the longitudinal section of Twoway valves, b () is the plan view (example 1: confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the valve seat surface observing (a) from axle L direction.
Figure 24 is the figure of the action of the Twoway valves that Figure 19 is described, a () is the longitudinal section of Twoway valves, b () is the plan view (example 2: confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the valve seat surface observing (a) from axle L direction.
Figure 25 is the figure of the action of the Twoway valves that Figure 19 is described, a () is the longitudinal section of Twoway valves, b () is the plan view (example 3: confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the valve seat surface observing (a) from axle L direction.
Figure 26 is the figure of the action of the Twoway valves that Figure 19 is described, a () is the longitudinal section of Twoway valves, b () is the plan view (example 4: confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the valve seat surface observing (a) from axle L direction.
Embodiment
(the first mode of execution)
Below, for the Twoway valves of the first mode of execution as rotary valve device of the present invention, with reference to Fig. 1 ~ Fig. 3, structure is described, and with reference to Fig. 4 ~ Fig. 9, action is described.
Fig. 1 is the longitudinal section of the Twoway valves of the first mode of execution of the present invention.Fig. 2 is the amplification view of a part for the Twoway valves being exaggerated Fig. 1.Fig. 3 is the sectional view of the X-X line along Fig. 1, a () represents that valve member is in the state (valve opening state) of the first stop position, b () represents that valve member is in the state (closing the valve closing state of the first valve port) of the second stop position, (c) represents that valve member is in the state (closing the valve closing state of the second valve port) of the 3rd stop position.In addition, the concept of " up and down " in below illustrating and corresponding up and down in Fig. 1, represent the relative position relationship of each parts, do not represent absolute position relationship.
The Twoway valves (in each figure, representing with symbol 1) of the first mode of execution is such as the loop that changes of the flow direction being disposed in fluid and for allowing or the Twoway valves of flowing etc. of limit fluid.
As shown in FIG. 1 to 3, the Twoway valves 1 of present embodiment has valve body 10, seat portion 20, valve member 30, seal ring 38, rotary shaft 40, rotary driving part 50 and helical spring 63.
Valve body 10 such as with stainless steel, aluminum alloy etc. for material and being formed, there is an end of top in the first portion 11 of substantially cylindrical shape and the figure of blocking first portion 11 and be installed on the roughly discoideus second portion 12 of this first portion 11 regularly.
At the central part of second portion 12, what be formed with this second portion 12 through overlooks rounded circular through hole 13.It is orthogonal with the valve seat surface 22a of seat portion 20 described later that this circular through hole 13 is set to its axle L.
Bearing insertion part 14 above in figure in circular through hole 13, insert the bearing portion 16 supported by rotary shaft 40 described later as rotating, and this bearing portion 16 is located at second portion 12 regularly.
And, the valve member support 15 of the Figure below in circular through hole 13, diameter holes portion 15a and hole portion, large footpath 15b is provided with side by side along axle L direction, wherein, path column part 31a in the cylindrical portion 31 of valve member 30 described later is fitting for rotating by diameter holes portion 15a, and hole portion, large footpath 15b is fitting for rotating by the large footpath column part 31b in this cylindrical portion 31 and diameter is larger than the diameter of diameter holes portion 15a.Further, between the inner peripheral surface 15a1 and the inner peripheral surface 15b1 of large hole, footpath portion 15b of diameter holes portion 15a, the support step surface 15c of orthogonal with above-mentioned inner peripheral surface 15a1 and inner peripheral surface 15b1 (comprising roughly orthogonal) is provided with.
Utilize the space in the inner space 11a of first portion 11 and the valve member support 15 of the circular through hole 13 of second portion 12 that is communicated with it, inside valve body 10, be formed with space Q.Sealed by seal ring 66 between first portion 11 and second portion 12, sealed by seal ring 67 between bearing portion 16 and second portion 12.
Seat portion 20 has: the seat portion main body 21 arranged integratedly with the mode of the other end of the Figure below of the first portion 11 of blocking valve main body 10 and this first portion 11; And be overlapped in regularly seat portion main body 21 towards the thin-plate member 22 in the plane of the Q side, space in valve body 10.
Further, seat portion 20 is provided with the first valve port P1 as two valve ports arranged in the mode of through seat portion main body 21 and thin-plate member 22 and the second valve port P2.In the present embodiment, under overlooking situation from the direction orthogonal with valve seat surface 22a, the first valve port P1 and the second valve port P2 to be configured in centered by axle L circumferentially.
The thin-plate member 22 of seat portion 20 is such as formed for material with stainless steel etc., possesses the plane valve seat surface 22a towards the space Q in valve body 10.This valve seat surface 22a is with arranged opposite at spaced intervals with the second portion 12 of valve body 10.
Valve member 30 has integratedly: cylindrical portion 31; And be located at the spool portion 33 of end (that is, one end of cylindrical portion 31) of Figure below of cylindrical portion 31.Valve member 30 is contained in the space Q in valve body 10.
Cylindrical portion 31 has integratedly: path column part 31a; And to be coaxially connected with path column part 31a and the diameter large footpath column part 31b larger than the diameter of this path column part 31a.Further, between the outer circumferential face 31a1 and the outer circumferential face 31b1 of large footpath column part 31b of path column part 31a, the cylindrical portion step surface 31c of orthogonal with above-mentioned outer circumferential face 31a1 and outer circumferential face 31b1 (comprising roughly orthogonal) is provided with.It is slightly less than the internal diameter of the diameter holes portion 15a of the valve member support 15 of above-mentioned valve body 10 that path column part 31a is formed as external diameter.Further, to be formed as external diameter slightly less than the internal diameter of hole portion, the large footpath 15b of the valve member support 15 of above-mentioned valve body 10 for large footpath column part 31b.Cylindrical portion 31 is embedded in valve member support 15 in the mode that its axle is overlapping with the axle L of circular through hole 13.Thus, cylindrical portion 31 (i.e. valve member 30) is supported as rotating around axle center by this valve member support 15.Cylindrical portion 31 is equivalent to an example in axle portion.In addition, path column part 31a, large footpath column part 31b and cylindrical portion step surface 31c are equivalent to an example of path shaft portion, large journal axle part and axle portion step surface respectively.
At the seal space R that outer circumferential face 31a1, the cylindrical portion step surface 31c of cylindrical portion 31 of the path column part 31a by cylindrical portion 31, the inner peripheral surface 15b1 of hole portion, large footpath 15b of valve member the support 15 and support step surface 15c of valve member support 15 impale, be equipped with seal ring 38.
Seal ring 38 is such as made up of the elastic material of nitrile butadiene rubber, silicone rubber geometric ratio softer.Seal ring 38 is formed as circular (ring-type) under the state (state of non-resiliently deformable) not from externally applied force.The internal diameter of seal ring 38 is formed as less than the external diameter of the path column part 31a of cylindrical portion 31, and the external diameter of seal ring 38 is formed as larger than the internal diameter of hole portion, the large footpath 15b of valve member support 15.Thus, if seal ring 38 is contained in above-mentioned seal space R, is extruded diametrically, and can seals between the outer circumferential face 31a1 of the path column part 31a of cylindrical portion 31 and the inner peripheral surface 15b1 of hole portion, the large footpath 15b of valve member support 15 rotatably.To the position of the cylindrical portion step surface 31c side of seal ring 38 (namely, the face of an other part for sealed member) be applied with hydrodynamic pressure in valve chamber B, and the hydrodynamic pressure position (that is, the face of a part for sealed member) of the support step surface 15c side of seal ring 38 is applied with in back pressure chamber H.Seal ring 38 is equivalent to an example of sealed member.
Further, the length of cylindrical portion 31 is identical with the length of the valve member support 15 of circular through hole 13 or slightly shorter than it, and the entirety of path column part 31a and a part of large footpath column part 31b are configured in this valve member support 15.Thus, upper-end surface 31d (that is, an end face of the path column part 31a) side above in the figure of cylindrical portion 31 forms airtight space (hereinafter referred to as " back pressure chamber H ").That is, valve member 30 arranges and is, end face 31d side thereon, and between the second portion 12 of valve body 10, form the back pressure chamber H gone out with the model split of a part of seal space Q.Further, by arranging valve member 30 in the Q of space, the inner space 11a of an other part of this space Q that is the first portion 11 of valve body 10 is divided as valve chamber B with back pressure chamber H.Spool portion 33 described later is held at the inner space 11a of this first portion 11.In other words, by by valve member 30 defined basis Q, and valve body 10 has the end side that is formed at cylindrical portion 31 and hold the valve chamber B in spool portion 33 and be formed at the back pressure chamber H of another side of cylindrical portion 31.
In addition, cylindrical portion 31 is provided with the rotary shaft mounting hole 32 of end 41 installation for rotary shaft 40 described later at upper-end surface 31d opening.The minor diameter part 32a of this rotary shaft mounting hole 32 and diameter large-diameter portion 32b larger than the diameter of minor diameter part is connected to form in the vertical direction.The diameter of minor diameter part 32a is slightly larger than the external diameter of an end 41 of rotary shaft 40.The diameter of large-diameter portion 32b is slightly larger than the external diameter of helical spring 63.
Spool portion 33 is formed as along the outstanding skirt shape of the radial direction of cylindrical portion 31, and is formed as roughly fan shape in the situation of overlooking of observing from axle L direction.In the present embodiment, spool portion 33 is conjointly arranged integratedly with one end of cylindrical portion 31.Certainly, except such structure, spool portion 33 also independently can be formed with cylindrical portion 31 phase, and conjointly arranges with one end of cylindrical portion 31 via connected element etc.Spool portion 33 is configured in the valve chamber B (inner space 11a) of valve body 10.The lower end surface 33a in spool portion 33 is formed as plane, can slide and closely be overlapped in the valve seat surface 22a of seat portion 20 rotatably.The airtight recess 34 of expansion inside this spool portion 33 is provided with at the lower end surface 33a in spool portion 33.
Airtight recess 34 is formed as the profile along spool portion 33 and hollows out the shape of the inner side in spool portion 33, in the situation of overlooking of observing from axle L direction, be formed as roughly fan shape.Airtight recess 34 by overlapping with valve seat surface 22a, and forms confined space G between this valve seat surface 22a.Cover the first valve port P1 or the second valve port P2 by spool portion 33 and expose in confined space G, mutually separating the first valve port P1 or the second valve port P2 thus, and be limited in the flowing of the fluid flowed between the first valve port P1 and the second valve port P2.
In addition, at valve member 30, be provided with and be communicated with the rotary shaft mounting hole 32 of cylindrical portion 31 and the Jun Ya road 36 of airtight recess 34.Utilize this Jun Ya road 36, connected confined space G (that is, by the first valve port P1 or the second valve port P2 of spool portion 33 opening and closing) and the back pressure chamber H of airtight recess 34 by rotary shaft mounting hole 32 in the mode be communicated with.In addition, in the present embodiment, valve member 30 is located on Jun Ya road 36, but is not limited thereto.Such as, in the structure of valve member 30 such as only opening and closing first valve port P1, the Jun Ya road of connection first valve port P1 and back pressure chamber H also can be set at valve body 10.
When valve member 30 is in the first stop position shown in Fig. 3 (a), do not utilize spool portion 33 to cover any one of the first valve port P1 and the second valve port P2, above-mentioned first valve port P1 and the second valve port P2 exposes and allows the flowing (valve opening state) of fluid in valve chamber B.
Further, if make valve member 30 rotate to the second stop position shown in Fig. 3 (b) from first stop position of Fig. 3 (a) along clockwise direction figure, then the first valve port P1 is covered by the spool portion 33 of valve member 30.Thus, first valve port P1 exposes in confined space G, second valve port P2 exposes in valve chamber B, and mutually separates the first valve port P1 or the second valve port P2, thus the flowing of the fluid flowed between the first valve port P1 and the second valve port P2 is restricted (valve closing state).
Further, if make valve member 30 counterclockwise rotate to the 3rd stop position shown in Fig. 3 (c) from first stop position of Fig. 3 (a) along figure, then the second valve port P2 is covered by the spool portion 33 of valve member 30.Thus, second valve port P2 exposes in confined space G, first valve port P1 exposes in valve chamber B, and mutually separates the first valve port P1 or the second valve port P2, thus the flowing of the fluid flowed between the first valve port P1 and the second valve port P2 is restricted (valve closing state).
At valve body 10 and valve member 30, be provided with and valve member 30 be rotated in a clockwise direction more than the second stop position and rotate more than the 3rd stop position a pair not shown rotary position-limit mechanism limited in the counterclockwise direction.Or, also can be following structure etc.: the detection unit be made up of the sensor of the angle of swing detecting valve member 30 etc. is set, and based on the angle of swing etc. of the valve member 30 detected by this detection unit, control rotary driving part 50 described later, stop at the second stop position and the 3rd stop position to make valve member 30.
Rotary shaft 40 is formed as cylindric, and an end 41 is installed on valve member 30, the second portion 12 of the through valve body 10 in the other end 42 and externally giving prominence to.Further, in the mode that the axle of rotary shaft 40 is overlapping with the axle L of circular through hole 13, the central part 43 of rotary shaft 40 is supported as rotating by the bearing portion 16 of the second portion 12 being located at valve body 10.
One end 41 of rotary shaft 40 is configured to, and inserts in the inner side of helical spring 63, and inserts at the rotary shaft mounting hole 32 of valve member 30.Now, helical spring 63 is clamped in compressive state to be located between the flange shape spring seat portions 44 of rotary shaft 40 and stepped part 32c, and this stepped part 32c is located between minor diameter part 32a in rotary shaft mounting hole 32 and large-diameter portion 32b.Thus, utilize helical spring 63 towards valve seat surface 22a push valve parts 30.Helical spring 63 is equivalent to an example of pressing component.
And, in an end 41 of rotary shaft 40, be provided with the not shown protuberance formed at its outer circumferential face, at the inner peripheral surface of the minor diameter part 32a of rotary shaft mounting hole 32, be provided with not shown recess, this recess is formed as locking in the sense of rotation centered by axle L for this protuberance.Thus, rotary shaft 40 can move along axle L direction relative to valve member 30, and if rotary shaft 40 rotate centered by axle L, then raised part with above-mentioned recess is locking and valve member 30 rotates together with rotary shaft 40.
At rotary shaft 40, with the figure of spring seat portions 44 in top the empty standard width of a room in an old-style house every mode be provided with the first lip part 45, and with the figure of the first lip part 45 in top the empty standard width of a room in an old-style house every mode be provided with the second lip part 46.First lip part 45 and the external diameter of the second lip part 46 roughly the same with the internal diameter of the bearing portion 16 of valve body 10.The first seal ring 61 is equipped between spring seat portions 44 and the first lip part 45, and between the first lip part 45 and the second lip part 46, be equipped with the second seal ring 62, utilize above-mentioned first seal ring 61 and seal between the second seal ring 62 pairs of bearing portions 16 and rotary shaft 40.
First seal ring 61 and the second seal ring 62 are such as made up of the elastic material of nitrile butadiene rubber, silicone rubber geometric ratio softer.First seal ring 61 and the second seal ring 62 are formed as circular (ring-type) under the state (state of non-resiliently deformable) not from externally applied force, its internal diameter is slightly less than the external diameter of the central part 43 of rotary shaft 40, and its external diameter is slightly larger than the internal diameter of bearing portion 16.
Rotary driving part 50 be arranged on rotary shaft 40 in the upper surface 12a of the second portion 12 of valve body 10 near the position of giving prominence to.Rotary driving part 50 has: the motor part 51 be made up of d.c. motor; Be installed on first gear 52 of the motor drive shaft 51a of motor part 51 regularly; And second gear 53 of the other end 42 of rotary shaft 40 is installed on regularly in the mode engaged with the first gear 52.If supply electric power to motor part 51, then rotary driving part 50 makes motor drive shaft 51a rotate, and this is rotated through the first gear 52 and the second gear 53 and rotary shaft 40 is rotated centered by axle L.In the present embodiment, form reducing gear by a pair gear (first gear 52 and the second gear 53), but also can form reducing gear by more gear.This reducing gear also can be made up of planetary pinion.
Next, be described with reference to the example of Fig. 4 ~ Fig. 9 to the action of the Twoway valves 1 of present embodiment.
Fig. 4 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming maximum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space max structure) of the valve member possessing (a).Fig. 5 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming minimum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space minimal structure) of the valve member possessing (a).
Fig. 6 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 1: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).Fig. 7 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 2: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).Fig. 8 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 3: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).Fig. 9 is the figure of the action of the Twoway valves of explanatory drawing 1, a () is the longitudinal section of Twoway valves, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 4: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
In above-mentioned Twoway valves 1, such as because of various essential factors such as the deformation caused by the figure tolerance of valve member 30, temperature variation, area of contact between the lower end surface 33a of valve member 30 and valve seat surface 22a can produce deviation or become unstable, thus the equilibrium of forces that the hydrodynamic pressure putting on valve member 30 produces changes.Therefore, using the deviation because of the area of contact between the lower end surface 33a of valve member 30 and valve seat surface 22a, confined space G becomes maximum situation and becomes minimum situation as most assignment example, the power of this valve member 30 of pushing produced by setting helical spring 63, even if also can not float from valve seat surface 22a at the situation valve member 30 of these most assignment examples, can, in whole examples of supposition, valve member 30 can not be made to float from valve seat surface 22a thus.
Such as, as shown in Fig. 4 (a), when valve member 30 is pushed on valve seat surface 22a by helical spring 63, think because of figure tolerance, the outer periphery 33a1 of the lower end surface 33a in spool portion 33 can be connected to valve seat surface 22a, and inner circumference edge 33a2 can leave from valve seat surface 22a.In this case, the lower end surface 33a in spool portion 33 is applied to the hydrodynamic pressure in confined space G.That is, as shown in Fig. 4 (b), the area S1 that overlooks being subject to the position of the hydrodynamic pressure in confined space G in valve member 30 becomes area (oblique line portion) in the outer periphery 33a1 of the lower end surface 33a in spool portion 33.Below, this structure is called " confined space max structure ".
And, as shown in Fig. 5 (a), when valve member 30 is pushed on valve seat surface 22a by helical spring 63, think because of figure tolerance, the inner circumference edge 33a2 of the lower end surface 33a in spool portion 33 can be connected to valve seat surface 22a, and outer periphery 33a1 can leave from valve seat surface 22a.In this case, the lower end surface 33a in spool portion 33 is applied to the hydrodynamic pressure in valve chamber B.That is, as shown in Fig. 5 (b), the area S2 that overlooks being subject to the position of the hydrodynamic pressure in confined space G in valve member 30 becomes area (oblique line portion) in the inner circumference edge 33a2 of the lower end surface 33a in spool portion 33.Below, this structure is called " confined space minimal structure ".
And, the situation higher than the hydrodynamic pressure in valve chamber B for the hydrodynamic pressure respectively in above-mentioned confined space max structure and confined space minimal structure, in confined space G and in back pressure chamber H and these four examples of low situation, below represent an example to the power that valve member 30 acts on.
In the following description, (namely the area SH1 that overlooks of the large footpath column part 31b of the cylindrical portion 31 of valve member 30 is set to 380 square millimeters, the diameter D1 of large footpath column part 31b is set to 22mm), (namely the area SH2 that overlooks of path column part 31a is set to 254.3 square millimeters, the diameter D2 of path column part 31a is set to 18mm), above-mentioned during confined space max structure is overlooked area S1 (, area in the outer periphery 33a1 of lower end surface 33a) be set to 385 square millimeters, above-mentioned during confined space minimal structure is overlooked area S2 (, area in the inner circumference edge 33a2 of lower end surface 33a) be set to 250 square millimeters.
And, the pressure difference Δ P1 of the above-mentioned hydrodynamic pressure when hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B is set to 3.0MPa, and the pressure difference Δ P2 of the above-mentioned hydrodynamic pressure when hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B is set to-3.0MPa.
The power F1 acted on valve member 30 by the hydrodynamic pressure in confined space G is obtained by the area (above-mentioned overlook area S1 or S2) of overlooking being subject to the position of the hydrodynamic pressure in the confined space G pressure difference (above-mentioned pressure difference Δ P1 or Δ P2) between the hydrodynamic pressure in the hydrodynamic pressure in confined space G and valve chamber B be multiplied by valve member 30.The power F2 acted on valve member 30 by the hydrodynamic pressure in back pressure chamber H is obtained by the area (above-mentioned overlook area SH1 or SH2) of overlooking being subject to the position of the hydrodynamic pressure in the back pressure chamber H pressure difference (above-mentioned pressure difference Δ P1 or Δ P2) between the hydrodynamic pressure in the hydrodynamic pressure in back pressure chamber H and valve chamber B be multiplied by valve member 30.Further, below by towards valve seat surface pushing valve member 30 towards being just set to.
(example 1: in confined space max structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B)
As shown in Fig. 6 (a), (b), the hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the cylindrical portion step surface 31c of the cylindrical portion 31 of valve member 30.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of large footpath column part 31b (that is, overlooking area SH1).Therefore, by the hydrodynamic pressure in confined space G, the power F1 that valve member 30 acts on is become:
F1＝(－ΔP1)×S1＝－1155[N]…(2－1)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 30 acts on is become:
F2＝ΔP1×SH1＝1140[N]…(2－2)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30:
F＝F1+F2＝－15[N]，
That is, to make valve member 30 have the power of 15 [N] from the mode effect that valve seat surface 22a floats.In this case, need to utilize helical spring 63 so that at least the power of [N] pushes valve member 30 towards valve seat surface 22a more than 15.
(example 2: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B)
As shown in Fig. 7 (a), (b), in example 2, also identical with example 1, apply the hydrodynamic pressure in back pressure chamber H in the position of large footpath column part 31b (that is, overlooking area SH1).Therefore, by the hydrodynamic pressure in confined space G, the power F1 that valve member 30 acts on is become:
F1＝(－ΔP1)×S2＝－750[N]…(2－3)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 30 acts on is become:
F2＝ΔP1×SH1＝1140[N]…(2－4)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30:
F＝F1+F2＝390[N]，
That is, the power of 390 [N] is had with mode effect valve member 30 being pushed on valve seat surface 22a.In this case, even if do not utilize helical spring 63 to push valve member 30 towards valve seat surface 22a, valve member 30 also can not float from valve seat surface 22a.
(example 3: in confined space max structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B)
As shown in Fig. 8 (a), (b), hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the support step surface 15c of the valve member support 15 of valve body 10.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of path column part 31a (that is, overlooking area SH2).Therefore, by the hydrodynamic pressure in confined space G, the power F1 that valve member 30 acts on is become:
F1＝(－ΔP2)×S1＝1155[N]…(2－5)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 30 acts on is become:
F2＝ΔP2×SH2＝－763[N]…(2－6)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30:
F＝F1+F2＝392[N]
That is, the power of 392 [N] is had with mode effect valve member 30 being pushed on valve seat surface 22a.In this case, even if do not utilize helical spring 63 to push valve member 30 towards valve seat surface 22a, valve member 30 also can not float from valve seat surface 22a.
(example 4: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B)
As shown in Fig. 9 (a), (b), in example 4, also identical with example 3, apply the hydrodynamic pressure in back pressure chamber H in the position of path column part 31a (that is, overlooking area SH2).Therefore, by the hydrodynamic pressure in confined space G, the power F1 that valve member 30 acts on is become:
F1＝(－ΔP2)×S2＝750[N]…(2－7)，
By the hydrodynamic pressure in back pressure chamber H, the power F2 that valve member 30 acts on is become:
F2＝ΔP2×SH2＝－763[N]…(2－8)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30:
F＝F1+F2＝－13[N]，
That is, to make valve member 30 have the power of 13 [N] from the mode effect that valve seat surface 22a floats.In this case, need to utilize helical spring 63 so that at least the power of [N] pushes valve member 30 towards valve seat surface 22a more than 13.
In above-mentioned example 1 ~ 4, in example 1, valve member 30 becomes maximum from the power that valve seat surface 22a floats.Therefore, in order to situation valve member 30 arbitrary in example 1 ~ 4 all can not float from valve seat surface 22a, in the example 1 as most assignment example, valve member 30 is not floated from valve seat surface 22a.That is, the power FS towards valve seat surface 22a pushing valve member 30 that helical spring 63 produces is set as at least exceeding the power that is 15 [N] that in example 1, valve member 30 are floated.And, by the relation between the hydrodynamic pressure of switch back pressure room H and the hydrodynamic pressure of valve chamber B, the area of overlooking being subject to the hydrodynamic pressure of back pressure chamber H in valve member 30 is changed.Specifically, the above-mentioned area of overlooking during hydrodynamic pressure height than back pressure chamber H of the hydrodynamic pressure of valve chamber B is SH2, and the above-mentioned area of the overlooking when hydrodynamic pressure of valve chamber B is lower than the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.Thus, this power set by helical spring 63 is less than structure in the past.
As mentioned above, in Twoway valves 1, the hydrodynamic pressure in confined space G and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the cylindrical portion step surface 31c of the cylindrical portion 31 of valve member 30.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of large footpath column part 31b (that is, overlooking area SH1).Further, the hydrodynamic pressure in confined space G and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the support step surface 15c of the valve member support 15 of valve body 10.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of path column part 31a (that is, overlooking area SH2).
That is, Twoway valves 1 is configured to, the area of overlooking being subject to the hydrodynamic pressure of back pressure chamber H in valve member 30 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B is SH2, above-mentioned area of overlooking during hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.And, between valve body 10 and valve member 30, be provided with the seal ring 38 to the ring-type sealed between them, and be configured to, when hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H, seal ring 38 is pushed on valve member 30, and seal ring 38 is pushed on valve body 10 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B.
As mentioned above, the Twoway valves 1 of present embodiment possesses: the valve body 10 being provided with space Q in inner side; Have space-oriented Q plane valve seat surface 22a and in the first valve port P1 of this valve seat surface 22a opening and the seat portion 20 of the second valve port P2; The mode being overlapped in valve seat surface 22a rotatably sliding to be configured in the Q of space and valve member 30 by rotating the connected relation switching the first valve port P1 and the second valve port P2 determined accordingly with stop position; And the helical spring 63 of valve member 30 is pushed towards valve seat surface 22a.Further, valve member 30 has: the cylindrical portion 31 that can be supported on valve body 10 around axle center rotatably; And to be connected with one end of cylindrical portion 31 and with the stop position opening and closing accordingly first valve port P1 of valve member 30 and the spool portion 33 of the second valve port P2.By by valve member 30 defined basis Q, and valve body 10 has the end side that is formed at cylindrical portion 31 and hold the valve chamber B in spool portion 33 and be formed at the back pressure chamber H of another side of cylindrical portion 31.Valve member 30 has the Jun Ya road 36 of connection first valve port P1 and the second valve port P2 and back pressure chamber H.Cylindrical portion 31 has: the path column part 31a configured towards the mode of back pressure chamber H with an end face; The large footpath column part 31b be connected coaxially with the other end of this path column part 31a; And the cylindrical portion step surface 31c be formed between the outer circumferential face 31a1 of path column part 31a and the outer circumferential face 31b1 of large footpath column part 31b.Valve body 10 has valve member support 15, and this valve member support 15 is provided with: the diameter holes portion 15a that can be fitted together to rotatably for path column part 31a; For hole portion, the large footpath 15b that large footpath column part 31b can be fitted together to rotatably; And the support step surface 15c be formed between the inner peripheral surface 15a1 of diameter holes portion 15a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.And, in the seal space R impaled by outer circumferential face 31a1, the cylindrical portion step surface 31c of path column part 31a, the inner peripheral surface 15b1 of large hole, footpath portion 15b and support step surface 15c, be provided with the seal ring 38 to the ring-type sealed between the outer circumferential face 31a1 of path column part 31a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.
Above, according to the present embodiment, the cylindrical portion 31 that can be supported on valve body 10 rotatably around axle center has: the path column part 31a configured towards the mode of back pressure chamber H with an end face; The large footpath column part 31b be connected coaxially with the other end of this path column part 31a; And the cylindrical portion step surface 31c be formed between the outer circumferential face 31a1 of path column part 31a and the outer circumferential face 31b1 of large footpath column part 31b.Further, valve body 10 has valve member support 15, and this valve member support 15 is provided with: the path column part 31a of cylindrical portion 31 is fitting for the diameter holes portion 15a that can rotate; The large footpath column part 31b of cylindrical portion 31 is fitting for hole portion, the large footpath 15b that can rotate; And the support step surface 15c be formed between the inner peripheral surface 15a1 of diameter holes portion 15a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.And, in the seal space R that inner peripheral surface 15b1 and the support step surface 15c of hole portion, the large footpath 15b of outer circumferential face 31a1, the cylindrical portion step surface 31c of the path column part 31a by cylindrical portion 31, the valve member support 15 of valve body 10 impale, be provided with the seal ring 38 to the ring-type sealed between the outer circumferential face 31a1 of path column part 31a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.Like this, be applied with the hydrodynamic pressure in valve chamber B in the position of the cylindrical portion step surface 31c side of seal ring 38, be applied with the hydrodynamic pressure in back pressure chamber H in the position of the support step surface 15c side of seal ring 38.Therefore, hydrodynamic pressure in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B, by the hydrodynamic pressure in back pressure chamber H, seal ring 38 is pushed on cylindrical portion step surface 31c, and the hydrodynamic pressure applied in the position in the inner part of the external diameter than large footpath column part 31b in the situation of overlooking in back pressure chamber H in valve member 30.And, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, by the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on support step surface 15c, and the hydrodynamic pressure applied than the external diameter of path column part 31a position in the inner part in the situation of overlooking in back pressure chamber H in valve member 30.That is, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, when making it the power of floating from valve seat surface 22a by the hydrodynamic pressure in back pressure chamber H to valve member 30 effect, because the area being subject to the position of the hydrodynamic pressure in back pressure chamber H in valve member 30 diminishes, so the power making valve member 30 float from valve seat surface 22a can be reduced.Thereby, it is possible to reduce the power pushing valve member 30 towards valve seat surface 22a that helical spring 63 produces, thus power valve member 30 being pushed on valve seat surface 22a can be suppressed.
And, Twoway valves 1 is configured to, the area of overlooking being subject to the hydrodynamic pressure of back pressure chamber H in valve member 30 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B is SH2, and the area of overlooking during hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.Like this, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, when making it the power of floating from valve seat surface 22a by the hydrodynamic pressure in back pressure chamber H to valve member 30 effect, due to the area being subject to the position of the hydrodynamic pressure in back pressure chamber H in valve member 30 (namely, overlook area) diminish, so the power making valve member 30 float from valve seat surface 22a can be reduced.Thereby, it is possible to reduce the power pushing valve member 30 towards valve seat surface 22a that helical spring 63 produces, thus power valve member 30 being pushed on valve seat surface 22a can be suppressed.
Further, between the valve body 10 and valve member 30 of Twoway valves 1, the seal ring 38 to the ring-type sealed between them is provided with.And be configured to, when hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H, seal ring 38 is pushed on valve member 30, and seal ring 38 is pushed on valve body 10 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B.Like this, for the seal ring 38 for the ring-type sealed between valve body 10 and valve member 30, be applied with the hydrodynamic pressure of back pressure chamber H in the face (position of support step surface 15c side) of its part, and be applied with the hydrodynamic pressure of valve chamber B in face (position of cylindrical portion step surface 31c side) a part of in addition.And, if seal ring 38 is pushed on valve member 30 when hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H, then also put on valve member 30 at the hydrodynamic pressure overlooking the back pressure chamber H that area applies in the face of a part for seal ring 38.Further, if seal ring 38 is pushed on valve body 10 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B, then the hydrodynamic pressure of the valve chamber B applied in the face of an other part for seal ring 38 also puts on valve body 10.That is be configured to, in valve member 30 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B be subject to the hydrodynamic pressure of back pressure chamber H overlook area be SH2 (, directly or be indirectly subject to power by sealed member overlook area), above-mentioned area of overlooking during hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.Like this, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, when making it the power of floating from valve seat surface 22a by the hydrodynamic pressure in back pressure chamber H to valve member 30 effect, due to the area being subject to the position of the hydrodynamic pressure in back pressure chamber H in valve member 30 (namely, overlook area) diminish, so the power making valve member 30 float from valve seat surface 22a can be reduced.Thereby, it is possible to reduce the power pushing valve member 30 towards valve seat surface 22a that helical spring 63 produces, thus power valve member 30 being pushed on valve seat surface 22a can be suppressed.
(the second mode of execution)
Below, for the flow channel switching valve of the second mode of execution as rotary valve device of the present invention, with reference to Figure 10, Figure 11, structure is described, and with reference to Figure 12 ~ Figure 17, action is described.
Figure 10 is the longitudinal section of the flow channel switching valve of the second mode of execution of the present invention.Figure 11 is the sectional view of the X-X line along Figure 10, and (a) represents that valve member is in the state of the first stop position, and (b) represents that valve member is in the state of the second stop position.In addition, the concept of " up and down " in the following description and corresponding up and down in Figure 11, represent the relative position relationship of each parts, do not represent absolute position relationship.
The flow channel switching valve (in each figure, representing with symbol 1A) of the second mode of execution is such as the loop that changes of the flow direction being disposed in fluid and the four-way switching valve of flow direction etc. for switch fluids.
As shown in Figure 10, Figure 11, the flow channel switching valve 1A of present embodiment has valve body 10, seat portion 20A, valve member 30A, seal ring 38, rotary shaft 40, rotary driving part 50 and helical spring 63.The flow channel switching valve 1A of present embodiment, except having seat portion 20A and valve member 30A except the seat portion 20 in the Twoway valves 1 replacing the first above-mentioned mode of execution and valve member 30, is the structure identical with the Twoway valves of the first above-mentioned mode of execution.Thus, in the following description, identical symbol marked to the structure identical with the first mode of execution and omit the description.
Seat portion 20A has: the seat portion main body 21 arranged integratedly with the mode of the other end of the Figure below of the first portion 11 of blocking valve main body 10 and this first portion 11; And be overlapped in regularly seat portion main body 21 towards the thin-plate member 22 in the plane of Q side, space.
Further, seat portion 20A is provided with as the first fixing port E1, the second fixing port E2 of the multiple valve ports arranged in the mode of through seat portion main body 21 and thin-plate member 22, the first switching port C1 and the second switching port C2.In the present embodiment, under overlooking situation from the direction orthogonal with valve seat surface 22a, first fixing port E1 is configured to overlapping with the axle L of circular through hole 13, and the second fixing port E2, the first switching port C1 and the second switching port C2 are configured in circumferentially (comprise probably circumferentially) centered by axle L.The seat portion main body 21 of seat portion 20A and thin-plate member 22 are the structures identical with the first above-mentioned mode of execution except the mouth offered.
Valve member 30A has integratedly: cylindrical portion 31; And be located at the spool portion 33A of end (that is, one end of cylindrical portion 31) of Figure below of cylindrical portion 31.Valve member 30A is contained in the space Q in valve body 10.Cylindrical portion 31 is structures identical with the first above-mentioned mode of execution.That is, the cylindrical portion 31 of present embodiment and the valve member support 15 of valve body 10 are structures identical with the first above-mentioned mode of execution shown in Fig. 2.
Spool portion 33A be formed as radial direction along cylindrical portion 31 outstanding overlook rounded shape, be configured in the inner space 11a of valve body 10.In the present embodiment, one end of spool portion 33A and cylindrical portion 31 is conjointly arranged integratedly.Certainly, except this structure, spool portion 33A also can be formed with cylindrical portion 31 phase independently, and conjointly arranges with one end of cylindrical portion 31 via connected element etc.The lower end surface 33a of spool portion 33A is formed as plane, can slide and closely be overlapped in the valve seat surface 22a of seat portion 20A rotatably.The airtight access 34A and open communication road 35 that expand inside this spool portion 33A is provided with at the lower end surface 33a of spool portion 33A.
Airtight access 34A is located at the lower end surface 33a of spool portion 33A with radially extending from middle body in the mode forming confined space G1 between valve seat surface 22a.In the present embodiment, in the situation of overlooking of observing from axle L direction, airtight access 34A is formed as banded (comprising roughly banded), and it has the extension 340 extended facing one direction in the outside of cylindrical portion 31.
Open communication road 35 is set to, and forms the space G2 of the roughly C word shape surrounding airtight access 34A at the lower end surface 33a of spool portion 33A.At spool portion 33A, be provided with the inside and outside attachment hole 33b connecting open communication road 35.
Further, at valve member 30A, be provided with and be communicated with the rotary shaft mounting hole 32 of cylindrical portion 31 and the Jun Ya road 36 of airtight access 34A.Utilize this Jun Ya road 36, connected confined space G1 and the back pressure chamber H of airtight access 34A by rotary shaft mounting hole 32 in the mode be communicated with.
When valve member 30A is in the first stop position shown in Figure 11 (a), connect the first fixing port E1 and the first switching port C1 by the confined space G1 of airtight access 34A in the mode be communicated with, and make the second fixing port E2 expose at the space G2 on open communication road 35 with the second switching port C2 and be connected these mouths in the mode be communicated with.And, rotate to the second stop position shown in Figure 11 (b) from first stop position of Figure 11 (a) if make it, then valve member 30A connects the first fixing port E1 and the second switching port C2 by the confined space G1 formed by airtight access 34A in the mode be communicated with, and makes the second fixing port E2 expose at the space G2 on open communication road 35 with the first switching port C1 and be connected these mouths in the mode be communicated with.
At valve body 10 and valve member 30A, be provided with a pair not shown rotary position-limit mechanism that limiting valve parts 30A rotates more than the first stop position and the second stop position.Or, also can be following structure: the detection unit be made up of the sensor of the angle of swing detecting valve member 30A etc. is set, and based on the angle of swing etc. of the valve member 30A detected by this detection unit, control rotary driving part 50 described later, stop at the first stop position and the second stop position to make valve member 30A.Thus, valve member 30A stops at the second stop position from the first stop position along counterclockwise rotating figure, and rotates along clockwise direction figure from the second stop position and stop at the first stop position.
Next, be described with reference to the example of Figure 12 ~ Figure 17 to the action of the flow channel switching valve 1A of present embodiment.
Figure 12 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming maximum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space max structure) of the valve member possessing (a).Figure 13 is the figure of the position of the hydrodynamic pressure illustrated in the confined space being subject to spool portion in valve member, a () is the sectional view of the valve member of the confined space in spool portion when becoming minimum, (b) is the plan view from axle L direction inspecting valve seat surface in the structure (in confined space minimal structure) of the valve member possessing (a).
Figure 14 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 1: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).Figure 15 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 2: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is higher than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).Figure 16 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 3: in confined space max structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).Figure 17 is the figure of the action of the flow channel switching valve that Figure 10 is described, a () is the longitudinal section of flow channel switching valve, b () is the plan view of the valve seat surface observing (a) from axle L direction, c () is the amplification view (example 4: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space and in back pressure chamber is lower than the hydrodynamic pressure in valve chamber) of the part being exaggerated (a).
In above-mentioned flow channel switching valve 1A, such as because of various essential factors such as the deformation caused by the figure tolerance of valve member 30A, temperature variation, area of contact between the lower end surface 33a of valve member 30A and valve seat surface 22a can produce deviation or become unstable, thus the equilibrium of forces that the hydrodynamic pressure putting on valve member 30A produces changes.Therefore, using the deviation because of the area of contact between the lower end surface 33a of valve member 30A and valve seat surface 22a, confined space G1 becomes maximum situation and becomes minimum situation as most assignment example, the power of this valve member of the pushing 30A produced by setting helical spring 63, even if also can not float from valve seat surface 22a at the situation valve member 30A of these most assignment examples, can, in whole examples of supposition, valve member 30 can not be made to float from valve seat surface 22a thus.
Such as, as shown in Figure 12 (a), when valve member 30A is pushed on valve seat surface 22a by helical spring 63, think because of figure tolerance, the outer periphery 33a3 of the part of the airtight access 34A of the encirclement in the lower end surface 33a of spool portion 33A can be connected to valve seat surface 22a, and the inner circumference edge 33a4 of this part can leave from valve seat surface 22a.In this case, this part of the lower end surface 33a of spool portion 33A is applied to the hydrodynamic pressure in confined space G1.That is, as shown in Figure 12 (b), the area S1 that overlooks being subject to the position of the hydrodynamic pressure in confined space G1 in valve member 30A becomes area (oblique line portion) in the outer periphery 33a3 of the part of the airtight access 34A of encirclement in the lower end surface 33a of spool portion 33A.Below, this structure is called " confined space max structure ".
And, as shown in Figure 13 (a), when valve member 30A is pushed on valve seat surface 22a by helical spring 63, think because of figure tolerance, the inner circumference edge 33a4 of the part of the airtight access 34A of the encirclement in the lower end surface 33a of spool portion 33A can be connected to valve seat surface 22a, and the outer periphery 33a3 of this part can leave from valve seat surface 22a.In this case, the hydrodynamic pressure in valve chamber B is applied to this part in the lower end surface 33a of spool portion 33A.That is, as shown in Figure 13 (b), the area S2 that overlooks being subject to the position of the hydrodynamic pressure in confined space G1 in valve member 30A becomes area (oblique line portion) in the inner circumference edge 33a4 of the part of the airtight access 34A of encirclement in the lower end surface 33a of spool portion 33A.Below, this structure is called " confined space minimal structure ".
And, the situation higher than the hydrodynamic pressure in valve chamber B for the hydrodynamic pressure respectively in above-mentioned confined space max structure and confined space minimal structure, in confined space G1 and in back pressure chamber H and these four examples of low situation, below represent an example of the power to valve member 30A effect.
In the following description, (namely the area SH1 that overlooks of the large footpath column part 31b of the cylindrical portion 31 of valve member 30A is set to 380 square millimeters, the diameter D1 of large footpath column part 31b is set to 22mm), (namely the area SH2 that overlooks of path column part 31a is set to 254.3 square millimeters, the diameter D2 of path column part 31a is set to 18mm), above-mentioned during confined space max structure is overlooked area S1 (, area in the outer periphery 33a3 of lower end surface 33a) be set to 400 square millimeters, above-mentioned during confined space minimal structure is overlooked area S2 (, area in the inner circumference edge 33a4 of lower end surface 33a) be set to 252 square millimeters.
And, the pressure difference Δ P1 of the above-mentioned hydrodynamic pressure when hydrodynamic pressure in confined space G1 and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B is set to 3.0MPa, and the pressure difference Δ P2 of the above-mentioned hydrodynamic pressure when hydrodynamic pressure in confined space G1 and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B is set to-3.0MPa.
By the hydrodynamic pressure in confined space G1, the power F1 of valve member 30A effect is obtained by the area (above-mentioned overlook area S1 or S2) of overlooking being subject to the position of the hydrodynamic pressure in the confined space G1 pressure difference (above-mentioned pressure difference Δ P1 or Δ P2) between the hydrodynamic pressure in the hydrodynamic pressure in confined space G1 and valve chamber B be multiplied by valve member 30A.By the hydrodynamic pressure in back pressure chamber H, the power F2 of valve member 30A effect is obtained by the area (above-mentioned overlook area SH1 or SH2) of overlooking being subject to the position of the hydrodynamic pressure in the back pressure chamber H pressure difference (above-mentioned pressure difference Δ P1 or Δ P2) between the hydrodynamic pressure in the hydrodynamic pressure in back pressure chamber H and valve chamber B be multiplied by valve member 30A.Further, below by push towards valve seat surface 22a valve member 30A towards being just set to.
(example 1: in confined space max structure, the situation that the hydrodynamic pressure in confined space G1 and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B)
As shown in Figure 14 (a), (b), the hydrodynamic pressure in confined space G1 and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the cylindrical portion step surface 31c of the cylindrical portion 31 of valve member 30A.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of large footpath column part 31b (that is, overlooking area SH1).Therefore, become by the power F1 of the hydrodynamic pressure in confined space G1 to valve member 30A effect:
F1＝(－ΔP1)×S1＝－1200[N]…(3－1)，
Become by the power F2 of the hydrodynamic pressure in back pressure chamber H to valve member 30A effect:
F2＝ΔP1×SH1＝1140[N]…(3－2)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30A:
F＝F1+F2＝－60[N]，
That is, to make valve member 30A have the power of 60 [N] from the mode effect that valve seat surface 22a floats.In this case, need to utilize helical spring 63 so that at least the power of [N] pushes valve member 30A towards valve seat surface 22a more than 60.
(example 2: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space G1 and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B)
As shown in Figure 15 (a), (b), in example 2, also identical with example 1, apply the hydrodynamic pressure in back pressure chamber H in the position of large footpath column part 31b (that is, overlooking area SH1).Therefore, become by the power F1 of the hydrodynamic pressure in confined space G1 to valve member 30A effect:
F1＝(－ΔP1)×S2＝－756[N]…(3－3)，
Become by the power F2 of the hydrodynamic pressure in back pressure chamber H to valve member 30A effect:
F2＝ΔP1×SH1＝1140[N]…(3－4)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30A:
F＝F1+F2＝384[N]，
That is, the power of 384 [N] is had with mode effect valve member 30A being pushed on valve seat surface 22a.In this case, even if do not utilize helical spring 63 to push valve member 30A towards valve seat surface 22a, valve member 30A also can not float from valve seat surface 22a.
(example 3: in confined space max structure, the situation that the hydrodynamic pressure in confined space G1 and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B)
As shown in Figure 16 (a), (b), hydrodynamic pressure in confined space G1 and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the support step surface 15c of the valve member support 15 of valve body 10.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of path column part 31a (that is, overlooking area SH2).Therefore, become by the power F1 of the hydrodynamic pressure in confined space G1 to valve member 30A effect:
F1＝(－ΔP2)×S1＝1200[N]…(3－5)，
Become by the power F2 of the hydrodynamic pressure in back pressure chamber H to valve member 30A effect:
F2＝ΔP2×SH2＝－763[N]…(3－6)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30A:
F＝F1+F2＝437[N]，
That is, the power of 437 [N] is had with mode effect valve member 30A being pushed on valve seat surface 22a.In this case, even if do not utilize helical spring 63 to push valve member 30A towards valve seat surface 22a, valve member 30A also can not float from valve seat surface 22a.
(example 4: in confined space minimal structure, the situation that the hydrodynamic pressure in confined space G1 and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B)
As shown in Figure 17 (a), (b), in example 4, also identical with example 3, apply the hydrodynamic pressure in back pressure chamber H in the position of path column part 31a (that is, overlooking area SH2).Therefore, become by the power F1 of the hydrodynamic pressure in confined space G1 to valve member 30A effect:
F1＝(－ΔP2)×S2＝756[N]…(3－7)，
Become by the power F2 of the hydrodynamic pressure in back pressure chamber H to valve member 30A effect:
F2＝ΔP2×SH2＝－763[N]…(3－8)。
Therefore, by above-mentioned formula, following power is acted on to valve member 30A:
F＝F1+F2＝－7[N]，
That is, to make valve member 30A have the power of 7 [N] from the mode effect that valve seat surface 22a floats.In this case, need to utilize helical spring 63 so that at least the power of [N] pushes valve member 30A towards valve seat surface 22a more than 7.
In above-mentioned example 1 ~ 4, in example 1, valve member 30A becomes maximum from the power that valve seat surface 22a floats.Therefore, in order to situation valve member 30A arbitrary in example 1 ~ 4 can not float from valve seat surface 22a, in the example 1 as most assignment example, valve member 30A is not floated from valve seat surface 22a.That is, the power FS towards valve seat surface 22a pushing valve member 30A that helical spring 63 produces is set as at least exceeding the power that is 60 [N] that in example 1, valve member 30A are floated.
For above-mentioned flow channel switching valve 1A, as structure in the past not cylindrical portion 31 arrange path column part 31a and large footpath column part 31b and throughout be axially the situation of uniform diameter (namely, the situation of above-mentioned SH2=SH1=380 square millimeter) under, if become the state of above-mentioned example 4, then become by the power F1 of the hydrodynamic pressure in confined space G1 to valve member 30A effect:
F1＝(－ΔP2)×S2＝756[N]…(3－9)，
Become by the power F2 of the hydrodynamic pressure in back pressure chamber H to valve member 30A effect:
F2＝ΔP2×SH2＝－1140[N]…(3－10)。
Therefore, by above-mentioned formula (23), (24), following power is acted on to valve member 30A:
F＝F1+F2＝－384[N]
That is, to make valve member 30A have the power of 384 [N] from the mode effect that valve seat surface 22a floats.In this case, need to utilize helical spring 63 so that at least the power of [N] pushes valve member 30A towards valve seat surface 22a more than 384, thus this example 4 become most assignment example.According to this situation, in the present embodiment, by the relation between the hydrodynamic pressure of switch back pressure room H and the hydrodynamic pressure of valve chamber B, the area of overlooking being subject to the hydrodynamic pressure of back pressure chamber H in valve member 30A is changed.Specifically, the above-mentioned area of overlooking during hydrodynamic pressure height than back pressure chamber H of the hydrodynamic pressure of valve chamber B is SH2, and the above-mentioned area of the overlooking when hydrodynamic pressure of valve chamber B is lower than the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.Thus, the power set by helical spring 63 is less than structure in the past.
As mentioned above, in flow channel switching valve 1A, the hydrodynamic pressure in confined space G1 and in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the cylindrical portion step surface 31c of the cylindrical portion 31 of valve member 30A.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of large footpath column part 31b (that is, overlooking area SH1).Further, the hydrodynamic pressure in confined space G1 and in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on the support step surface 15c of the valve member support 15 of valve body 10.Therefore, the hydrodynamic pressure in back pressure chamber H is applied in the position of path column part 31a (that is, overlooking area SH2).
That is, flow channel switching valve 1A is configured to, the area of overlooking being subject to the hydrodynamic pressure of back pressure chamber H in valve member 30A when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B is SH2, above-mentioned area of overlooking during hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.And, between valve body 10 and valve member 30A, be provided with the seal ring 38 to the ring-type sealed between them, and be configured to, when hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H, seal ring 38 is pushed on valve member 30A, and seal ring 38 is pushed on valve body 10 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B.
As mentioned above, the flow channel switching valve 1A of present embodiment possesses: the valve body 10 being provided with space Q in inner side; There is the seat portion 20A of the plane valve seat surface 22a of space-oriented Q, the first fixing port E1, the second fixing port E2, the first switching port C1 and the second switching port C2 at this valve seat surface 22a opening; The mode being overlapped in valve seat surface 22a rotatably sliding to be configured in the Q of space and valve member 30A by rotating the connected relation switching the first fixing port E1, the second fixing port E2, the first switching port C1 and the second switching port C2 that determine accordingly with stop position; And the helical spring 63 of valve member 30A is pushed towards valve seat surface 22a.Further, valve member 30A has: the cylindrical portion 31 that can be supported on valve body 10 around axle center rotatably; And to be connected with one end of cylindrical portion 31 and to be provided with the spool portion 33A of airtight access 34A, this airtight access 34A is formed confined space G1 and is communicated with the first fixing port E1, the second fixing port E2, the first switching port C1 and the second switching port C2 that regulation combines by this confined space G1 with the stop position of valve member 30A accordingly between valve seat surface 22a.By by valve member 30A defined basis Q, and valve body 10 has the end side that is formed at cylindrical portion 31 and hold the valve chamber B of spool portion 33A and be formed at the back pressure chamber H of another side of cylindrical portion 31.Valve member 30A has the Jun Ya road 36 connecting airtight access 34A and back pressure chamber H.Cylindrical portion 31 has: the path column part 31a configured towards the mode of back pressure chamber H with an end face; The large footpath column part 31b be connected coaxially with the other end of this path column part 31a; And the cylindrical portion step surface 31c be formed between the outer circumferential face 31a1 of path column part 31a and the outer circumferential face 31b1 of large footpath column part 31b.Valve body 10 has valve member support 15, and this valve member support 15 is provided with: path column part 31a is fitting for the diameter holes portion 15a that can rotate; Large footpath column part 31b is fitting for hole portion, the large footpath 15b that can rotate; And the support step surface 15c be formed between the inner peripheral surface 15a1 of diameter holes portion 15a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.And, in the seal space R impaled by outer circumferential face 31a1, the cylindrical portion step surface 31c of path column part 31a, the inner peripheral surface 15b1 of large hole, footpath portion 15b and support step surface 15c, be provided with the seal ring 38 to the ring-type sealed between the outer circumferential face 31a1 of path column part 31a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.
Above, according to the present embodiment, the cylindrical portion 31 that can be supported on valve body 10 rotatably around axle center has: the path column part 31a configured towards the mode of back pressure chamber H with an end face; The large footpath column part 31b be connected coaxially with the other end of this path column part 31a; And the cylindrical portion step surface 31c be formed between the outer circumferential face 31a1 of path column part 31a and the outer circumferential face 31b1 of large footpath column part 31b.Further, valve body 10 has valve member support 15, and this valve member support 15 is provided with: the path column part 31a of cylindrical portion 31 is fitting for the diameter holes portion 15a that can rotate; The large footpath column part 31b of cylindrical portion 31 is fitting for hole portion, the large footpath 15b that can rotate; And the support step surface 15c be formed between the inner peripheral surface 15a1 of diameter holes portion 15a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.And, in the seal space R that inner peripheral surface 15b1 and the support step surface 15c of hole portion, the large footpath 15b of outer circumferential face 31a1, the cylindrical portion step surface 31c of the path column part 31a by cylindrical portion 31, the valve member support 15 of valve body 10 impale, be provided with the seal ring 38 to the ring-type sealed between the outer circumferential face 31a1 of path column part 31a and the inner peripheral surface 15b1 of large hole, footpath portion 15b.Like this, be applied with the hydrodynamic pressure in valve chamber B in the position of the cylindrical portion step surface 31c side of seal ring 38, be applied with the hydrodynamic pressure in back pressure chamber H in the position of the support step surface 15c side of seal ring 38.Therefore, hydrodynamic pressure in back pressure chamber H is higher than the hydrodynamic pressure in valve chamber B, by the hydrodynamic pressure in back pressure chamber H, seal ring 38 is pushed on cylindrical portion step surface 31c, and the hydrodynamic pressure applied in the position in the inner part of the external diameter than large footpath column part 31b in the situation of overlooking in back pressure chamber H in valve member 30A.And, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, by the hydrodynamic pressure in valve chamber B, seal ring 38 is pushed on support step surface 15c, and the hydrodynamic pressure applied than the external diameter of path column part 31a position in the inner part in the situation of overlooking in back pressure chamber H in valve member 30A.That is, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, when making it the power of floating from valve seat surface 22a by the hydrodynamic pressure in back pressure chamber H to valve member 30A effect, because the area being subject to the position of the hydrodynamic pressure in back pressure chamber H in valve member 30A diminishes, so the power making valve member 30A float from valve seat surface 22a can be reduced.Thereby, it is possible to reduce the power pushing valve member 30A towards valve seat surface 22a that helical spring 63 produces, thus power valve member 30A being pushed on valve seat surface 22a can be suppressed.
And, flow channel switching valve 1A is configured to, the area of overlooking being subject to the hydrodynamic pressure of back pressure chamber H in valve member 30A when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B is SH2, area of overlooking during hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.Like this, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, when making it the power of floating from valve seat surface 22a by the hydrodynamic pressure in back pressure chamber H to valve member 30A effect, due to the area being subject to the position of the hydrodynamic pressure in back pressure chamber H in valve member 30A (namely, overlook area) diminish, so the power making valve member 30A float from valve seat surface 22a can be reduced.Thereby, it is possible to reduce the power pushing valve member 30A towards valve seat surface 22a that helical spring 63 produces, thus power valve member 30A being pushed on valve seat surface 22a can be suppressed.
Further, between the valve body 10 and valve member 30A of flow channel switching valve 1A, the seal ring 38 to the ring-type sealed between them is provided with.And be configured to, when hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H, seal ring 38 is pushed on valve member 30A, and seal ring 38 is pushed on valve body 10 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B.Like this, for the seal ring 38 for the ring-type sealed between valve body 10 and valve member 30A, be applied with the hydrodynamic pressure of back pressure chamber H in the face (position of support step surface 15c side) of its part, and be applied with the hydrodynamic pressure of valve chamber B in face (position of cylindrical portion step surface 31c side) a part of in addition.And, if seal ring 38 is pushed on valve member 30A when hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H, then also put on valve member 30A at the hydrodynamic pressure overlooking the back pressure chamber H that area applies in the face of a part for seal ring 38.Further, if seal ring 38 is pushed on valve body 10 when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B, then the hydrodynamic pressure of the valve chamber B applied in the face of an other part for seal ring 38 also puts on valve body 10.That is be configured to, in valve member 30A when the hydrodynamic pressure of back pressure chamber H is lower than the hydrodynamic pressure of valve chamber B be subject to the hydrodynamic pressure of back pressure chamber H overlook area be SH2 (, directly or be indirectly subject to power by sealed member overlook area), above-mentioned area of overlooking during hydrodynamic pressure height than valve chamber B of the hydrodynamic pressure of back pressure chamber H is that SH1, SH2 are less than SH1.Like this, hydrodynamic pressure in back pressure chamber H is lower than the hydrodynamic pressure in valve chamber B, when making it the power of floating from valve seat surface 22a by the hydrodynamic pressure in back pressure chamber H to valve member 30A effect, due to the area being subject to the position of the hydrodynamic pressure in back pressure chamber H in valve member 30A (namely, overlook area) diminish, so the power making valve member 30A float from valve seat surface 22a can be reduced.Thereby, it is possible to reduce the power pushing valve member 30A towards valve seat surface 22a that helical spring 63 produces, thus power valve member 30A being pushed on valve seat surface 22a can be suppressed.
Above, for the present invention, enumerate and be preferred embodiment illustrated, but rotary valve device of the present invention is not limited to the structure of above-mentioned mode of execution.
Such as, above-mentioned first mode of execution is the structure being provided with airtight recess 34 at the lower end surface 33a in the spool portion 33 of valve member 30, but is not limited thereto, and also can be set to by lower end surface 33a plane and eliminate the structure of airtight recess 34.In the case of such a construction, when lower end surface 33a is overlapping with the first valve port P1 or the second valve port P2, in the mode connecting above-mentioned valve port and back pressure chamber H communicatively, the one end on Jun Ya road 36 is configured at lower end surface 33a.
Further, above-mentioned second mode of execution is the flow channel switching valve (four-way switching valve) of switching four streams, but is not limited thereto, such as, also can be the structure of switching three streams, the flow channel switching valve switching the structure of the stream of more than five.Further, the present invention also may be used for the control valve unit being communicated with and blocking two streams.
Further, in the above-described 2nd embodiment, being the structure with an airtight access, but being not limited thereto, also can be the structure with plural airtight access.Such as, in the above-described embodiment, also can omit valve member 30 attachment hole 33b and using open communication road 35 as airtight access.
And, in the above-described 2nd embodiment, it is the structure being provided with airtight access 34A and open communication road 35 at the spool portion 33A of valve member 30, such as, but being not limited thereto, also can be only arrange airtight access 34A at spool portion 33A and delete the structure of the position forming open communication road 35.Even such structure eliminating open communication road 35, in each stop position of valve member 30A, expose the second fixing port E2 and the side be not communicated with the first fixing port E1 in the first switching port C1 and the second switching port C2 in an other part of valve chamber B that is inner space 11a and be connected these mouths in the mode be communicated with, thus the connected relation of valve port can be switched.
Further, in the respective embodiments described above, being the structure being provided with Jun Ya road 36 at valve member 30 and valve member 30A, but being not limited thereto, also can be the structure being provided with Jun Ya road at valve body 10.
Further, in the respective embodiments described above, there is the first seal ring 61 and the second seal ring 62 be made up of more soft elastic material, but be not limited thereto.Such as, form at the synthetic resin that also can compare hard by fluororesin etc. such as teflon (PTFE) by the second seal ring 62 of the exterior arrangement of valve body 10 than the first seal ring 61, only otherwise violate object of the present invention, the structure of the first seal ring 61 and the second seal ring 62 is arbitrary.Further, if only just fully sealing can be guaranteed with the first seal ring 61, then also can be the structure of omission second seal ring 62.
In addition, above-mentioned mode of execution only represents the mode of representative of the present invention, and the present invention is not limited to mode of execution.That is, those skilled in the art are according to known opinion in the past, can implement with various distortion without departing from the spirit and scope of the invention.Even if because of such distortion, as long as also possess the structure of rotary valve device of the present invention, be certainly included in category of the present invention.
The explanation of symbol
1-Twoway valves (rotary valve device), 1A-flow channel switching valve (rotary valve device), 10-valve body, 15-valve member support, 15a-diameter holes portion, the inner peripheral surface in 15a1-diameter holes portion, 15b-large hole, footpath portion, the inner peripheral surface in 15b1-large hole, footpath portion, 15c-support step surface, 20, 20A-seat portion, 22a-valve seat surface, 30, 30A-valve member, 31-cylindrical portion (axle portion), 31a-path column part (path shaft portion), the outer circumferential face of 31a1-path column part, 31b-large footpath column part (large journal axle part), the outer circumferential face of 31b1-large footpath column part, 31c-cylindrical portion step surface (axle portion step surface), the upper-end surface of 31d-cylindrical portion, 32-rotary shaft mounting hole, 33, 33A-spool portion, the lower end surface in 33a-spool portion, the outer periphery of 33a1-lower end surface, the inner circumference edge of 33a2-lower end surface, the outer periphery of the part of the airtight access of the encirclement in 33a3-lower end surface, the inner circumference edge of the part of the airtight access of the encirclement in 33a4-lower end surface, 34-airtight recess, 34A-airtight access, 36-Jun Ya road, 38-seal ring (sealed member), 40-rotary shaft, 50-rotary driving part, 63-helical spring (pressing component), B-valve chamber, C1-the first switching port (valve port), C2-the second switching port (valve port), F1-the first fixing port (valve port), F2-the second fixing port (valve port), G, G1-confined space, H-back pressure chamber, P1-the first valve port, P2-the second valve port, the space of the inner side of Q-valve body, R-seal space is (by the outer circumferential face of path shaft portion, axle portion step surface, the space that the inner peripheral surface in hole portion, large footpath and support step surface impale), the axle of L-circular through hole.

Claims (6)

1. a rotary valve device, possesses: valve body, and it is provided with space in inner side; Seat portion, it has the plane valve seat surface towards above-mentioned space and two valve ports at this valve seat surface opening; Valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, by rotating the connected relation switching above-mentioned two valve ports determined accordingly with stop position; And pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface,
The feature of above-mentioned rotary valve device is,
Above-mentioned valve member has: axle portion, and it can be supported on above-mentioned valve body rotatably around axle center; And spool portion, it is located at the one end in above-mentioned axle portion, and with at least one valve port in above-mentioned two valve ports of above-mentioned stop position opening and closing accordingly,
Above-mentioned valve body by dividing above-mentioned space by above-mentioned valve member, thus has the end side that is formed at above-mentioned axle portion and holds the valve chamber in above-mentioned spool portion and be formed at the back pressure chamber of another side in above-mentioned axle portion,
Above-mentioned valve body or above-mentioned valve member have connect in above-mentioned two valve ports by the valve port of above-mentioned spool portion opening and closing and the Jun Ya road of above-mentioned back pressure chamber,
Be configured to, in above-mentioned valve member when the hydrodynamic pressure of above-mentioned back pressure chamber is lower than the hydrodynamic pressure of above-mentioned valve chamber be subject to the hydrodynamic pressure of above-mentioned back pressure chamber overlook area, it is little that above-mentioned during the hydrodynamic pressure height of the hydrodynamic pressure comparing above-mentioned back pressure chamber than above-mentioned valve chamber overlooks area.
2. a rotary valve device, possesses: valve body, and it is provided with space in inner side; Seat portion, it has the plane valve seat surface towards above-mentioned space and the multiple valve ports at this valve seat surface opening; Valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, by rotating the connected relation switching the above-mentioned multiple valve port determined accordingly with stop position; And pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface,
The feature of above-mentioned rotary valve device is,
Above-mentioned valve member has: axle portion, and it can be supported on above-mentioned valve body rotatably around axle center; And spool portion, it is located at the one end in above-mentioned axle portion, and be provided with one or more airtight access, this one or more airtight access forms confined space between above-mentioned valve seat surface, and be communicated with above-mentioned multiple valve port that regulation combines accordingly with above-mentioned stop position by this confined space
Above-mentioned valve body by dividing above-mentioned space by above-mentioned valve member, thus has the end side that is formed at above-mentioned axle portion and holds the valve chamber in above-mentioned spool portion and be formed at the back pressure chamber of another side in above-mentioned axle portion,
Above-mentioned valve body or above-mentioned valve member have the Jun Ya road of any one and the above-mentioned back pressure chamber connected in above-mentioned airtight access,
Be configured to, in above-mentioned valve member when the hydrodynamic pressure of above-mentioned back pressure chamber is lower than the hydrodynamic pressure of above-mentioned valve chamber be subject to the hydrodynamic pressure of above-mentioned back pressure chamber overlook area, it is little that above-mentioned during the hydrodynamic pressure height of the hydrodynamic pressure comparing above-mentioned back pressure chamber than above-mentioned valve chamber overlooks area.
3. rotary valve device according to claim 1 and 2, is characterized in that,
Between above-mentioned valve body and above-mentioned valve member, be provided with the sealed member to the ring-type sealed between them,
And be configured to, when hydrodynamic pressure height than above-mentioned valve chamber of the hydrodynamic pressure of above-mentioned back pressure chamber, above-mentioned sealed member is pushed on above-mentioned valve member, and above-mentioned sealed member is pushed on above-mentioned valve body when the hydrodynamic pressure of above-mentioned back pressure chamber is lower than the hydrodynamic pressure of above-mentioned valve chamber.
4. rotary valve device according to claim 3, is characterized in that,
The above-mentioned axle portion of above-mentioned valve member has: path shaft portion, and it configures in the mode of an end face towards above-mentioned back pressure chamber; Large journal axle part, it is connected coaxially with the other end of this path shaft portion; And axle portion step surface, it is formed between the outer circumferential face of above-mentioned path shaft portion and the outer circumferential face of above-mentioned large journal axle part,
Above-mentioned valve body has valve member support, and this valve member support is provided with: diameter holes portion, and above-mentioned path shaft portion is fitting for rotating by it; Hole portion, large footpath, above-mentioned large journal axle part is fitting for rotating by it; And support step surface, it is formed between the inner peripheral surface in above-mentioned diameter holes portion and the inner peripheral surface in large hole, footpath portion,
Above-mentioned sealed member is arranged in the space that impaled by the inner peripheral surface in the outer circumferential face of above-mentioned path shaft portion, above-mentioned axle portion step surface, hole portion, above-mentioned large footpath and above-mentioned support step surface, to seal between the outer circumferential face of above-mentioned path shaft portion and the inner peripheral surface in hole portion, above-mentioned large footpath.
5. a rotary valve device, possesses: valve body, and it is provided with space in inner side; Seat portion, it has the plane valve seat surface towards above-mentioned space and two valve ports at this valve seat surface opening; Valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, by rotating the connected relation switching above-mentioned two valve ports determined accordingly with stop position; And pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface,
The feature of above-mentioned rotary valve device is,
Above-mentioned valve member has: cylindrical portion, and it can be supported on above-mentioned valve body rotatably around axle center; And spool portion, it is connected with one end of above-mentioned cylindrical portion, and with at least one valve port in above-mentioned two valve ports of above-mentioned stop position opening and closing accordingly,
Above-mentioned valve body by dividing above-mentioned space by above-mentioned valve member, thus has the end side that is formed at above-mentioned cylindrical portion and holds the valve chamber in above-mentioned spool portion and be formed at the back pressure chamber of another side of above-mentioned cylindrical portion,
Above-mentioned valve body or above-mentioned valve member have connect in above-mentioned two valve ports by the valve port of above-mentioned spool portion opening and closing and the Jun Ya road of above-mentioned back pressure chamber,
Above-mentioned cylindrical portion has: path column part, and it configures in the mode of an end face towards above-mentioned back pressure chamber; Large footpath column part, it is connected coaxially with the other end of this path column part; And cylindrical portion step surface, it is formed between the outer circumferential face of above-mentioned path column part and the outer circumferential face of above-mentioned large footpath column part,
Above-mentioned valve body has valve member support, and this valve member support is provided with: diameter holes portion, and above-mentioned path column part is fitting for rotating by it; Hole portion, large footpath, above-mentioned large footpath column part is fitting for rotating by it; And support step surface, it is formed between the inner peripheral surface in above-mentioned diameter holes portion and the inner peripheral surface in large hole, footpath portion,
In the space that inner peripheral surface and the above-mentioned support step surface by the outer circumferential face of above-mentioned path column part, above-mentioned cylindrical portion step surface, hole portion, above-mentioned large footpath impales, be provided with the sealed member to the ring-type sealed between the outer circumferential face of above-mentioned path column part and the inner peripheral surface in hole portion, above-mentioned large footpath.
6. a rotary valve device, possesses: valve body, and it is provided with space in inner side; Seat portion, it has the plane valve seat surface towards above-mentioned space and the multiple valve ports at this valve seat surface opening; Valve member, its mode being overlapped in above-mentioned valve seat surface rotatably sliding is configured in above-mentioned space, by rotating the connected relation switching the above-mentioned multiple valve port determined accordingly with stop position; And pressing component, it pushes above-mentioned valve member towards above-mentioned valve seat surface,
The feature of above-mentioned rotary valve device is,
Above-mentioned valve member has: cylindrical portion, and it can be supported on above-mentioned valve body rotatably around axle center; And spool portion, it is connected with one end of above-mentioned cylindrical portion, and be provided with one or more airtight access, this one or more airtight access forms confined space between above-mentioned valve seat surface, and be communicated with above-mentioned multiple valve port that regulation combines accordingly with above-mentioned stop position by this confined space
Above-mentioned valve body by dividing above-mentioned space by above-mentioned valve member, thus has the end side that is formed at above-mentioned cylindrical portion and holds the valve chamber in above-mentioned spool portion and be formed at the back pressure chamber of another side of above-mentioned cylindrical portion,
Above-mentioned valve body or above-mentioned valve member have the Jun Ya road of any one and the above-mentioned back pressure chamber connected in above-mentioned airtight access,
Above-mentioned cylindrical portion has: path column part, and it configures in the mode of an end face towards above-mentioned back pressure chamber; Large footpath column part, it is connected coaxially with the other end of this path column part; And cylindrical portion step surface, it is formed between the outer circumferential face of above-mentioned path column part and the outer circumferential face of above-mentioned large footpath column part,
Above-mentioned valve body has valve member support, and this valve member support is provided with: diameter holes portion, and above-mentioned path column part is fitting for rotating by it; Hole portion, large footpath, above-mentioned large footpath column part is fitting for rotating by it; And support step surface, it is formed between the inner peripheral surface in above-mentioned diameter holes portion and the inner peripheral surface in large hole, footpath portion,
In the space that inner peripheral surface and the above-mentioned support step surface by the outer circumferential face of above-mentioned path column part, above-mentioned cylindrical portion step surface, hole portion, above-mentioned large footpath impales, be provided with the sealed member to the ring-type sealed between the outer circumferential face of above-mentioned path column part and the inner peripheral surface in hole portion, above-mentioned large footpath.
CN201380074846.3A 2013-03-22 2013-12-05 Rotary valve device Active CN105190136B (en)

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PCT/JP2013/082704 WO2014147897A1 (en) 2013-03-22 2013-12-05 Rotary valve device

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CN110686089A (en) * 2016-06-03 2020-01-14 日本电产三协株式会社 Valve device
CN112189108A (en) * 2018-06-04 2021-01-05 株式会社不二工机 Flow path switching valve
CN113202953A (en) * 2020-01-31 2021-08-03 株式会社鹭宫制作所 Rotary switching valve
CN114688304A (en) * 2020-12-25 2022-07-01 株式会社鹭宫制作所 Rotary switching valve

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JP6510810B2 (en) * 2014-12-26 2019-05-08 株式会社不二工機 Flow path switching valve
JP6969895B2 (en) 2017-05-09 2021-11-24 日本電産サンキョー株式会社 Valve device
CN117957390A (en) 2021-09-21 2024-04-30 伊格尔工业股份有限公司 Switching valve
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