CN104197089A - Rotary type fluid passage changeover valve - Google Patents
Rotary type fluid passage changeover valve Download PDFInfo
- Publication number
- CN104197089A CN104197089A CN201410457649.6A CN201410457649A CN104197089A CN 104197089 A CN104197089 A CN 104197089A CN 201410457649 A CN201410457649 A CN 201410457649A CN 104197089 A CN104197089 A CN 104197089A
- Authority
- CN
- China
- Prior art keywords
- cavity
- spool
- pressure channel
- communicated
- flow path
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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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
- F16K11/08—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only taps or cocks
-
- 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
- F16K5/00—Plug valves; Taps or cocks comprising only cut-off apparatus having at least one of the sealing faces shaped as a more or less complete surface of a solid of revolution, the opening and closing movement being predominantly rotary
- F16K5/08—Details
Abstract
The invention provides a rotary type fluid passage changeover valve. The rotary type fluid passage changeover valve comprises a valve body, a valve element, a driving device and an elastic part, wherein the valve body is provided with a valve cavity; the valve element is arranged in the valve cavity in a rotatable mode, and a high-pressure channel and a low-pressure channel which are independent of each other are formed between the valve element and the side walls of the valve body; the driving device is located at the first end of the valve element and is in drive connection with the valve element so as to drive the valve element to rotate; the elastic part is located at the second end of the valve element and abuts against the valve body and the valve element respectively, a first cavity is formed between the first end of the valve element and the valve body, a second cavity and a third cavity which are independent of each other are formed between the second end of the valve element and the valve body, and the third cavity is located in the outer side of the circumferential direction of the second cavity; at least one of the first cavity, the second cavity and the third cavity is communicated with the high-pressure channel, and the remaining cavities of the first cavity, the second cavity and the third cavity are communicated with the low-pressure channel. The problems of increase of input torque of a motor and abrasion to moving parts in the prior art are effectively solved according to the technical scheme.
Description
Technical field
The present invention relates to switching valve technical field, in particular to a kind of rotary flow path switching valve.
Background technique
In the prior art, rotary flow path switching valve utilizes drive unit to realize the lifting of spool and the compression of spool, thereby realizes the switching of switching valve and the sealing that resets.Drive unit comprises motor and driving mechanism, and drive mechanism transmission is passed through in the rotation of the commutation process dependence motor of switching valve, realization is converted.
Rotary flow path switching valve is due to the existence of internal leakage, and the upper and lower cavity that spool and valve body are formed has pressure and produces, and the air pressure in this upper and lower cavity is between high low pressure.Spool is under the effect of this air pressure, there is one to be adjacent to making a concerted effort of valve body, and the working principle of switching valve is lifting and the compression that drives spool by mechanical transmission, therefore existing scheme need overcome this atmospheric pressure and could realize and make the disengaging of spool and valve body in commutation.Certainly will require like this moment of torsion and the power of motor input larger, electric machine structure is larger, causes the physical dimension of product large, weight is large, cost is high.Meanwhile, due to the existence of this atmospheric pressure, in commutation, due to the impact being stressed, the wearing and tearing of each moving element also can aggravate, and are unfavorable for the long-term use of product, have also reduced the reliability of product.In addition, due to the impact of atmospheric pressure, finish in commutation, spool is replied while being adjacent to valve body again, can produce noise, and atmospheric pressure is larger, and noise also will be larger.
Summary of the invention
The present invention aims to provide a kind of rotary flow path switching valve, to solve in prior art due to the uncertain input torque that causes increasing motor of air pressure between spool and the upper and lower cavity of valve body formation, the problem of moving element wearing and tearing.
To achieve these goals, the invention provides a kind of rotary flow path switching valve, comprising: valve body, there is valve pocket, valve pocket is cone table shape; Spool, suitable with valve pocket shape, spool is arranged in valve pocket rotationally, between spool and the sidewall of valve body, forms separate high-pressure channel and low-pressure channel, spool has along the first end of its axial direction and the second end, and the area of the first end of spool is less than the area of the second end of spool; Drive unit, is positioned at the first end of spool and drives and be connected to drive valve core rotation with spool; Elastic component, be positioned at the second end of spool, and distinguish butt with valve body and spool, between the first end of spool and valve body, form the first cavity, between the second end of spool and valve body, form the second separate cavity and the 3rd cavity, the week that the 3rd cavity is positioned at the second cavity laterally; At least one cavity in the first cavity, the second cavity and the 3rd cavity is communicated with high-pressure channel, and remaining cavity in the first cavity, the second cavity and the 3rd cavity is communicated with low-pressure channel.
Further, one in the second cavity and the 3rd cavity is communicated with high-pressure channel, and another in the second cavity and the 3rd cavity is communicated with low-pressure channel.
Further, high-pressure channel is all communicated with the first cavity and the 3rd cavity, and low-pressure channel is communicated with the second cavity, and the cross-section area S of the second cavity
1meet the following conditions: S
1≤ S
3, wherein, S
3for the half of the first end surface area of spool and the difference of the second end surface area.
Further, the cross-section area S of the second cavity
1meet the following conditions: 0.8S
3≤ S
1≤ S
3, wherein, S
3for the half of the first end surface area of spool and the difference of the second end surface area.
Further, low-pressure channel is all communicated with the first cavity and the 3rd cavity, and high-pressure channel is communicated with the second cavity, and the cross-section area S of the second cavity
1meet the following conditions: S
3≤ S
1, wherein, S
3for the half of the first end surface area of spool and the difference of the second end surface area.
Further, the cross-section area S of the second cavity
1meet the following conditions: S
3≤ S
1≤ 1.2S
3, wherein, S
3for the half of the first end surface area of spool and the difference of the second end surface area.
Further, spool comprises the first disk body, the second disk body and the separating part between the first disk body and the second disk body, and the first disk body forms the first end of spool, and the second disk body forms the second end of spool.
Further, on the first disk body, be formed with the first intercommunicating pore that is communicated with high-pressure channel and the first cavity, on the second disk body, be formed with the second intercommunicating pore that is communicated with high-pressure channel and the 3rd cavity.
Further, the dead in line of the axis of the first intercommunicating pore and the second intercommunicating pore.
Further, on separating part, be formed with the third connecting hole that is communicated with low-pressure channel and the second cavity.
Further, third connecting hole comprises interconnective radial hole section and axial bore section, the axis of axial bore section and the dead in line of spool.
Apply technological scheme of the present invention, the first cavity, the second cavity and the 3rd cavity are communicated with high-pressure channel or low-pressure channel respectively, make like this pressure at least one cavity in the above-mentioned first to the 3rd cavity equate with the pressure in high-pressure channel, pressure in all the other cavitys equates with the pressure in low-pressure channel, the pressure in three cavitys can be decided like this.Because the pressure in the stressed of spool and the above-mentioned first to the 3rd cavity is relevant, simultaneously also with the size of spool about (being specially the cross-section area of the first end surface area of spool and the difference of the second end surface area and the second cavity).Like this, according to force analysis, derive calculate can to spool be subject to first to the 3rd cavity internal air pressure make a concerted effort design.When above-mentioned while making a concerted effort to be designed to zero, the initial stage of commutation is that the driving force of the process need of spool disengaging valve body will reduce (only need overcome the active force of elasticity recovery part) greatly, correspondingly, drive output power and the moment of torsion etc. of motor used to reduce significantly, and then the size of motor entirety will be reduced greatly, cost also can decrease.Owing to needing pretightening force to seal between spool and valve body, so consider the factor such as machining error, spool is stressed, and to be slightly larger than zero pair of rotary flow path switching valve favourable.Meanwhile, the stressed direction of spool should be identical with the elastic force direction of elastic component.As shown in the above, rotary flow path switching valve of the present invention can solve effectively due to the uncertain problem that causes the input torque that increases motor of air pressure between spool and the upper and lower cavity of valve body formation.On the other hand, due in the process of whole commutation, the atmospheric pressure that makes spool be adjacent to valve body has been balanced, so in the later stage of commutation, when spool is adjacent to valve body again, also just can not produce very large impact force.The moment of spool and valve body butt like this, the Strike note sending also just correspondingly reduces.And the reducing of impact force, to component because the potential damage that shock produces also just greatly reduces.
Brief description of the drawings
The Figure of description that forms the application's a part is used to provide a further understanding of the present invention, and schematic description and description of the present invention is used for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 shows the vertical profile schematic diagram according to the embodiment of rotary flow path switching valve of the present invention;
Fig. 2 shows the A place enlarged diagram of the rotary flow path switching valve of Fig. 1;
Fig. 3 shows the structural representation of the spool of the rotary flow path switching valve of Fig. 1;
Fig. 4 shows the elevational schematic view of the spool of Fig. 3; And
Fig. 5 shows the schematic top plan view of the spool of Fig. 3.
Wherein, above-mentioned accompanying drawing comprises the following drawings mark:
10, valve body; 20, spool; 21, the first disk body; 211, the first intercommunicating pore; 22, the second disk body; 221, the second intercommunicating pore; 23, separating part; 231, third connecting hole; 30, elastic component; 41, the first cavity; 42, the second cavity; 43, the 3rd cavity.
Embodiment
It should be noted that, in the situation that not conflicting, the feature in embodiment and embodiment in the application can combine mutually.Describe below with reference to the accompanying drawings and in conjunction with the embodiments the present invention in detail.
As shown in Figures 1 to 5, the rotary flow path switching valve of the present embodiment comprises: valve body 10, spool 20, drive unit and elastic component 30.In said structure, valve body 10 has valve pocket, valve pocket is cone table shape, spool 20 is suitable with valve pocket shape, spool 20 is arranged in valve pocket rotationally, between the sidewall of spool 20 and valve body 10, form separate high-pressure channel and low-pressure channel, spool 20 has along the first end of its axial direction and the second end, and the area of the first end of spool 20 is less than the area of the second end of spool.Drive unit is positioned at the first end of spool 20 and drives and be connected to drive spool 20 to rotate with spool 20, and elastic component 30 is positioned at the second end of spool 20, and distinguishes butts with valve body 10 and spool 20.Between the first end of spool 20 and valve body 10, form the first cavity 41, between the second end of spool 20 and valve body 10, form week that the second separate cavity 42 and the 3rd cavity 43, the three cavitys 43 are positioned at the second cavity 42 laterally.At least one cavity in the first cavity 41, the second cavity 42 and the 3rd cavity 43 is communicated with high-pressure channel, and remaining cavity in the first cavity 41, the second cavity 42 and the 3rd cavity 43 is communicated with low-pressure channel.
The technological scheme of application the present embodiment, the first cavity 41, the second cavity 42 and the 3rd cavity 43 are communicated with high-pressure channel or low-pressure channel respectively, make like this pressure at least one cavity in the above-mentioned first to the 3rd cavity equate with the pressure in high-pressure channel, pressure in all the other cavitys equates with the pressure in low-pressure channel, the pressure in three cavitys can be decided like this.Because the pressure in the stressed of spool 20 and the above-mentioned first to the 3rd cavity is relevant, simultaneously also with the size of spool 20 about (being specially the cross-section area of the first end surface area of spool 20 and the difference of the second end surface area and the second cavity).Like this, according to force analysis, derive calculate can to spool 20 be subject to first to the 3rd cavity internal air pressure make a concerted effort design.When above-mentioned while making a concerted effort to be designed to zero, the initial stage of commutation is that the driving force of the process need of spool disengaging valve body will reduce (only need overcome the active force of elasticity recovery part) greatly, correspondingly, drive output power and the moment of torsion etc. of motor used to reduce significantly, and then the size of motor entirety will be reduced greatly, cost also can decrease.Owing to needing pretightening force to seal between spool 20 and valve body 10, so consider the factor such as machining error, spool 20 is stressed, and to be slightly larger than zero pair of rotary flow path switching valve favourable.Meanwhile, the stressed direction of spool 20 should be identical with the elastic force direction of elastic component.As shown in the above, rotary flow path switching valve of the present invention can solve effectively due to the uncertain problem that causes the input torque that increases motor of air pressure between spool and the upper and lower cavity of valve body formation.On the other hand, due in the process of whole commutation, the atmospheric pressure that makes spool be adjacent to valve body has been balanced, so in the later stage of commutation, when spool 20 is adjacent to valve body again, also just can not produce very large impact force.The moment of spool 20 and valve body 10 butts like this, the Strike note sending also just correspondingly reduces.And the reducing of impact force, to component because the potential damage that shock produces also just greatly reduces.
For the ease of the pressure control in the first to the 3rd cavity, need to make the pressure in the second cavity 42 be different from the pressure in the 3rd cavity 43.,, when the second cavity 42 is communicated with high-pressure channel, the 3rd cavity 43 is communicated with low-pressure channel.When the 3rd cavity 43 is communicated with low-pressure channel, the 3rd cavity 43 is communicated with high-pressure channel.
In the present embodiment, high-pressure channel is all communicated with the first cavity 41 and the 3rd cavity 43, and low-pressure channel is communicated with the second cavity 42, and the cross-section area S of the second cavity 42
1meet the following conditions:
S
1≤ S
3, wherein, S
3for the half of the first end surface area of spool 20 and the difference of the second end surface area.
In the present embodiment, high-pressure channel is all communicated with the first cavity 41 and the 3rd cavity 43, makes like this air pressure in the first cavity 41 and the 3rd cavity 43 equate with the air pressure in high-pressure channel.Low-pressure channel is communicated with the second cavity 42, and the air pressure in such the second cavity 42 equates with the air pressure in low-pressure channel.Known through derivation calculating, the stressed cross-section area S that depends on the second cavity 42 of spool 20
1half S with the first end surface area of spool 20 and the difference of the second end surface area
3between difference, that is to say, in the time that both are equal, the initial stage of commutation is that the driving force of spool 20 process need that departs from valve body 10 will reduce (only need overcome the active force of elasticity recovery part 30) greatly, correspondingly, drive output power and the moment of torsion etc. of motor used to reduce significantly, and then the size of motor entirety will be reduced greatly, cost also can decrease.Owing to needing pretightening force to seal between spool 20 and valve body 10, so consider the factor such as machining error, spool 20 is stressed, and to be slightly larger than 0 pair of rotary flow path switching valve favourable, namely needs S
1and S
3between the certain difference of existence.Meanwhile, the stressed direction of spool 20 should be identical with the elastic force direction of elastic component 30, i.e. S
1≤ S
3.As shown in the above, the rotary flow path switching valve of the present embodiment can solve effectively due to the uncertain problem that causes the input torque that increases motor of air pressure between spool and the upper and lower cavity of valve body formation.On the other hand, due in the process of whole commutation, the atmospheric pressure that makes spool 20 be adjacent to valve body 10 has been balanced, so in the later stage of commutation, when spool 20 is adjacent to valve body 10 again, also just can not produce very large impact force.The moment of spool 20 and valve body 10 butts like this, the Strike note sending also just correspondingly reduces.And the reducing of impact force, to component because the potential damage that shock produces also just greatly reduces.From the angle of reliability, promote widely the reliability of product.
For a person skilled in the art, above-mentioned technical Analysis, can understand the cross-section area S of the second cavity defining in this patent
1, spool first end and the second end surface area S
2/ S
3, all refer to the useful area that produces pressure and change (area on the projection plane of vertical and axial direction).
As shown in Figure 1, in the present embodiment, valve pocket is up-small and down-big taper type, and corresponding, spool 20 is also up-small and down-big taper type, and the first end surface area of spool 20 is less than the second end surface area of spool 20.In the present embodiment, spool 20 comprises that the first disk body 21, the second disk body 22 and separating part 23, the first disk bodies 21 between the first disk body 21 and the second disk body 22 form the first end of spool 20, and the second disk body 22 forms the second end of spool 20.In the present embodiment, elastic component 30 is positioned at the second cavity 42, and elastic component 30 is spring.Certainly, elastic component also can be arranged in the 3rd cavity 43.
Next in conjunction with Fig. 1 to Fig. 5, the force analysis of spool 20 is described in detail.
The first cavity 41 and the 3rd cavity 43 internal air pressures are high pressure P
1, spool 20 both sides are high pressure P on one side
1, be low pressure P on one side
2, the second cavity 42 internal air pressures that form between spool 20 and the bottom of valve body 10 are low pressure P
2.Therefore air pressure can be equivalent to five power shown in Fig. 3 for the active force of spool, and above-mentioned five power are specific as follows:
F
1: the air pressure P in the second cavity 42 forming between spool 20 and the bottom of valve body 10
2to the active force of spool 20, upwards, size is P to direction
2s
1, wherein S
1it is the cross-section area of the second cavity 42;
F
2: the air pressure P of the 3rd cavity 43 forming between spool 20 and the bottom of valve body 10
1to the active force of spool, upwards, size is P to direction
1s
2, wherein S
2it is the cross-section area of the 3rd cavity 43;
F
3: the equivalent action power of the low-pressure channel of spool 20 to spool 20, this equivalence active force equals the active force of low-pressure channel to the first disk body 21 and low-pressure channel to the difference between the active force of the second disk body 22, and direction is downward, big or small P
2s
3, S
3for the half of the first end surface area of spool 20 and the difference of the second end surface area;
F
4: the air pressure P of the first cavity 41 forming between spool 20 and valve body 10
1to the active force of spool 20, direction is downward, and size is P
1s
4, wherein S
4for the first end surface area of spool 20;
F
5: the equivalent action power of the high-pressure channel of spool 20 to spool, this equivalence active force equals the active force of high-pressure channel to the first disk body 21 and low-pressure channel to the difference between the active force of the second disk body 22, and direction is downward, big or small P
1s
3, S
5for the half of the first end surface area of spool 20 and the difference of the second end surface area.
Suppose that active force is upwards for just, the F=F that makes a concerted effort of spool 20
1+ F
2-F
3-F
4-F
5=P
2s
1+ P
1s
2-P
2s
3-P
1s
4-P
1s
3=P
1(S
2-S
4-S
3)+P
2(S
1-S
3).As known in Fig. 3 to Fig. 5, S
2+ S
1=S
4+ 2S
3, F=P
1(S
3-S
1)+P
2(S
1-S
3)=(P
1-P
2) (S
3-S
1).
From the reversing principle of rotary flow path switching valve, the movement process of spool 20 is for first departing from valve body 10, then half-twist, and then be adjacent to valve body 10.Can learn from movement process, if S
3=S
1f=0, the initial stage of commutation is that the driving force of spool 20 process need that departs from valve body will reduce (only need overcome the active force of elasticity recovery part 30) greatly so.Can reduce significantly with respect to the output power and the moment of torsion etc. that drive motor used.According to the feature of motor, along with reducing of power and moment of torsion, the size of motor entirety will reduce greatly, thereby the profile of whole product, weight all can be reduced accordingly, thereby reach miniaturization, light-weighted object, on cost, also just obtained reducing widely.Because spool 20 and valve body 10 need pretightening force upwards to seal, so consider machining error, make a concerted effort to be slightly larger than 0 pair of this product favourable, i.e. S
1≤ S
3.Further preferably, 0.8S
3≤ S
1≤ S
3.
In like manner, in not shown mode of execution, low-pressure channel is all communicated with the first cavity 41 and the 3rd cavity 43, and high-pressure channel is communicated with the second cavity 42, and the cross-section area S of the second cavity 42
1meet the following conditions:
S
3≤S
1,
Wherein, S
3for the half of the first end surface area of spool 20 and the difference of the second end surface area.Can ensure that like this pretightening force that spool 20 can obtain upwards seals.Further preferably, S
3≤ S
1≤ 1.2S
3.
On the other hand, due in the process of whole commutation, the atmospheric pressure that makes spool 20 be adjacent to valve body 10 has been balanced, so in the later stage of commutation, when spool 20 is adjacent to valve body 10 again, also just can not produce very large impact force, the moment of spool 20 and valve body 10 butts like this, the Strike note sending also just correspondingly reduces.And the reducing of impact force, to component because the potential damage that shock produces also just greatly reduces, from the angle of reliability, also just promoted widely the reliability of product, particularly the situations that adopt soft seal for spool 20 and valve body 10, situation about sealing by the flexible material such as rubber, plastics.
In the present embodiment, on the first disk body 21, be formed with the second intercommunicating pore 221 that is formed with connection high-pressure channel and the 3rd cavity 43 on the first intercommunicating pore 211, the second disk bodies 22 that are communicated with high-pressure channel and the first cavity 41.Above-mentioned the first intercommunicating pore 211 and the second intercommunicating pore 221 are easy to process, easily realize.
As shown in Figure 3, in the present embodiment, the first intercommunicating pore 211 and the second intercommunicating pore 221 are axial hole.For the ease of processing, as shown in Figure 3, the dead in line of the axis of the first intercommunicating pore 211 and the second intercommunicating pore 221.
As shown in Figure 3, in the present embodiment, on separating part 23, be formed with the third connecting hole 231 that is communicated with low-pressure channel and the second cavity 42.Above-mentioned third connecting hole 231 is arranged on separating part 23 can not bring adverse effect to the intensity of spool 20.For convenient processing, as shown in Figure 3, in the present embodiment, third connecting hole 231 comprises interconnective radial hole section and axial bore section, the dead in line of the axis of axial bore section and spool 20.
Certainly, one skilled in the art will appreciate that as other feasible mode of executions, also can make the first cavity 41, the 3rd cavity 43 be communicated with low-pressure channel, and the second cavity 42 is communicated with high-pressure channel.Or also can make the first cavity 41, the second cavity 42 be communicated with low-pressure channel, and the 3rd cavity 43 is communicated with high-pressure channel.In above-mentioned mode of execution, need to limit S according to concrete stressing conditions
1and S
3size, do not repeat them here.
As can be seen from the above description, the above embodiments of the present invention have realized following technique effect:
Adopt the air pressure that structure of the present invention can balance valve core, spool is not stressed under air pressure, thereby reduce input torque and the power of motor, realize the miniaturization of motor.Finally reduce product overall space size and product weight, reduce product cost and promote reliability simultaneously.
The foregoing is only the preferred embodiments of the present invention, be not limited to the present invention, for a person skilled in the art, the present invention can have various modifications and variations.Within the spirit and principles in the present invention all, any amendment of doing, be equal to replacement, improvement etc., within all should being included in protection scope of the present invention.
Claims (11)
1. a rotary flow path switching valve, comprising:
Valve body (10), has valve pocket, and described valve pocket is cone table shape;
Spool (20), suitable with described valve pocket shape, described spool (20) is arranged in described valve pocket rotationally, between the sidewall of described spool (20) and described valve body (10), form separate high-pressure channel and low-pressure channel, described spool (20) has along the first end of its axial direction and the second end, and the area of the first end of described spool (20) is less than the area of the second end of described spool (20);
Drive unit, is positioned at the first end of described spool (20) and drives and be connected to drive described spool (20) to rotate with described spool (20);
Elastic component (30), is positioned at the second end of described spool (20), and distinguishes butt with described valve body (10) and described spool (20),
It is characterized in that,
Between the first end of described spool (20) and described valve body (10), form the first cavity (41), between the second end of described spool (20) and described valve body (10), form separate the second cavity (42) and the 3rd cavity (43), the week that described the 3rd cavity (43) is positioned at described the second cavity (42) laterally;
At least one cavity in described the first cavity (41), described the second cavity (42) and described the 3rd cavity (43) is communicated with described high-pressure channel, and remaining cavity in described the first cavity (41), described the second cavity (42) and described the 3rd cavity (43) is communicated with described low-pressure channel.
2. rotary flow path switching valve according to claim 1, it is characterized in that, one in described the second cavity (42) and described the 3rd cavity (43) is communicated with described high-pressure channel, and another in described the second cavity (42) and described the 3rd cavity (43) is communicated with described low-pressure channel.
3. rotary flow path switching valve according to claim 1, it is characterized in that, described high-pressure channel is all communicated with described the first cavity (41) and described the 3rd cavity (43), described low-pressure channel is communicated with described the second cavity (42), and the cross-section area S of described the second cavity (42)
1meet the following conditions:
S
1≤S
3,
Wherein, described S
3for the half of the first end surface area of spool (20) and the difference of the second end surface area.
4. rotary flow path switching valve according to claim 3, is characterized in that, the cross-section area S of described the second cavity (42)
1meet the following conditions:
0.8S
3≤S
1≤S
3,
Wherein, described S
3for the half of the first end surface area of spool (20) and the difference of the second end surface area.
5. rotary flow path switching valve according to claim 1, it is characterized in that, described low-pressure channel is all communicated with described the first cavity (41) and described the 3rd cavity (43), described high-pressure channel is communicated with described the second cavity (42), and the cross-section area S of described the second cavity (42)
1meet the following conditions:
S
3≤S
1,
Wherein, described S
3for the half of the first end surface area of spool (20) and the difference of the second end surface area.
6. rotary flow path switching valve according to claim 5, is characterized in that, the cross-section area S of described the second cavity (42)
1meet the following conditions:
S
3≤S
1≤1.2S
3,
Wherein, described S
3for the half of the first end surface area of spool (20) and the difference of the second end surface area.
7. rotary flow path switching valve according to claim 1, it is characterized in that, described spool (20) comprise the first disk body (21), the second disk body (22) and be positioned at described the first disk body (21) and described the second disk body (22) between separating part (23), described the first disk body (21) forms the first end of described spool (20), and described the second disk body (22) forms the second end of described spool (20).
8. rotary flow path switching valve according to claim 7, it is characterized in that, on described the first disk body (21), be formed with the first intercommunicating pore (211) that is communicated with described high-pressure channel and described the first cavity (41), on described the second disk body (22), be formed with the second intercommunicating pore (221) that is communicated with described high-pressure channel and described the 3rd cavity (43).
9. rotary flow path switching valve according to claim 8, is characterized in that, the dead in line of the axis of described the first intercommunicating pore (211) and described the second intercommunicating pore (221).
10. rotary flow path switching valve according to claim 7, is characterized in that, is formed with the third connecting hole (231) that is communicated with described low-pressure channel and described the second cavity (42) on described separating part (23).
11. rotary flow path switching valves according to claim 10, it is characterized in that, described third connecting hole (231) comprises interconnective radial hole section and axial bore section, the dead in line of the axis of described axial bore section and described spool (20).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201410457649.6A CN104197089A (en) | 2014-09-10 | 2014-09-10 | Rotary type fluid passage changeover valve |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201410457649.6A CN104197089A (en) | 2014-09-10 | 2014-09-10 | Rotary type fluid passage changeover valve |
Publications (1)
Publication Number | Publication Date |
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CN104197089A true CN104197089A (en) | 2014-12-10 |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105987202A (en) * | 2015-02-16 | 2016-10-05 | 浙江三花旋转阀有限公司 | Rotary flow path switching valve |
CN109210237A (en) * | 2017-06-30 | 2019-01-15 | 杭州三花研究院有限公司 | Volume control device |
CN111322432A (en) * | 2018-12-14 | 2020-06-23 | 盾安环境技术有限公司 | Six-way valve |
WO2023103288A1 (en) * | 2021-12-10 | 2023-06-15 | 浙江盾安人工环境股份有限公司 | Five-way valve |
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JPH09217849A (en) * | 1996-02-09 | 1997-08-19 | Nippon Boorubarubu Kk | Quantitative feed pole valve |
CN201250924Y (en) * | 2008-09-12 | 2009-06-03 | 江苏九龙阀门制造有限公司 | High-pressure and ultra-low temperature four-way ball valve |
CN201386831Y (en) * | 2009-02-13 | 2010-01-20 | 浙江石化阀门有限公司 | Four-way ball valve |
CN102966762A (en) * | 2012-12-06 | 2013-03-13 | 银川东方运输设备有限公司 | Improved rotary four-way fluid reversing valve |
CN202971994U (en) * | 2012-12-10 | 2013-06-05 | 广东明珠流体机械有限公司 | Cross metallic seal ball valve |
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Publication number | Priority date | Publication date | Assignee | Title |
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JPH09217849A (en) * | 1996-02-09 | 1997-08-19 | Nippon Boorubarubu Kk | Quantitative feed pole valve |
CN201250924Y (en) * | 2008-09-12 | 2009-06-03 | 江苏九龙阀门制造有限公司 | High-pressure and ultra-low temperature four-way ball valve |
CN201386831Y (en) * | 2009-02-13 | 2010-01-20 | 浙江石化阀门有限公司 | Four-way ball valve |
CN102966762A (en) * | 2012-12-06 | 2013-03-13 | 银川东方运输设备有限公司 | Improved rotary four-way fluid reversing valve |
CN202971994U (en) * | 2012-12-10 | 2013-06-05 | 广东明珠流体机械有限公司 | Cross metallic seal ball valve |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN105987202A (en) * | 2015-02-16 | 2016-10-05 | 浙江三花旋转阀有限公司 | Rotary flow path switching valve |
CN105987202B (en) * | 2015-02-16 | 2019-11-12 | 浙江三花旋转阀有限公司 | Rotary flow path switching valve |
CN109210237A (en) * | 2017-06-30 | 2019-01-15 | 杭州三花研究院有限公司 | Volume control device |
CN111322432A (en) * | 2018-12-14 | 2020-06-23 | 盾安环境技术有限公司 | Six-way valve |
WO2023103288A1 (en) * | 2021-12-10 | 2023-06-15 | 浙江盾安人工环境股份有限公司 | Five-way valve |
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