CN202789552U - Discharge valve and compressor comprising same - Google Patents
Discharge valve and compressor comprising same Download PDFInfo
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- CN202789552U CN202789552U CN 201220470547 CN201220470547U CN202789552U CN 202789552 U CN202789552 U CN 202789552U CN 201220470547 CN201220470547 CN 201220470547 CN 201220470547 U CN201220470547 U CN 201220470547U CN 202789552 U CN202789552 U CN 202789552U
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Abstract
The utility model relates to an exhaust valve (10A, 10B, 10C, 10D, 10E), include: the valve comprises a valve body (12), wherein a fluid inlet (15) is arranged at the first end of the valve body, at least one fluid outlet (17) communicated with the fluid inlet in a fluid mode and a valve plate (20) used for opening or closing the fluid outlet are arranged on the side wall of the valve body, and the axial direction of the fluid outlet is inclined relative to the axial direction of the fluid inlet. The utility model discloses still relate to a compressor including above-mentioned discharge valve. The utility model discloses a lower fluid resistance that has of discharge valve to can show to reduce because the pressure drop that discharge valve leads to in the compressor that has adopted this discharge valve, thereby improve the operating efficiency of compressor.
Description
Technical field
The utility model relates to a kind of outlet valve and comprises the compressor of this outlet valve.
Background technique
As described in Figure 1, conventional scroll compressor 100 generally comprise housing 110, be arranged on housing 110 1 ends top cover 112, be arranged on the bottom 114 of housing 110 the other ends and be arranged on top cover 112 and housing 110 between be separated into the dividing plate 116 of high pressure side and low voltage side with the inner space with compressor.Consist of the high pressure side between dividing plate 116 and the top cover 112, and consist of low voltage side between dividing plate 116, housing 110 and the bottom 114.Be provided with for the air input joint (not shown) that sucks fluid in low voltage side, be provided with the exhaust joint 119 for the fluid after discharging compression in the high pressure side.Be provided with the motor 120 that is consisted of by stator 122 and rotor 124 in the housing 110.Be provided with live axle 130 in the rotor 124 to drive the compressing mechanism that consists of by deciding vortex 150 and moving vortex 160.Moving vortex 160 comprises end plate 164, be formed on the hub section 162 of end plate one side and be formed on the spiral helicine blade 166 of end plate opposite side.Deciding vortex 150 comprises end plate 154, is formed on the spiral helicine blade 156 of end plate one side and is formed on the relief opening 152 of the substantial middle position of end plate.One side of moving vortex 160 is supported by main bearing seat 140, and an end of live axle 130 is also supported by main bearing seat 140.One end of live axle 130 is provided with eccentric crank pin 132, is provided with unloading lining 142 between the hub section 162 of eccentric crank pin 132 and moving vortex 160.Driving by motor 140, moving vortex 160 will be with respect to deciding vortex 150 translation rotations (namely, the central axis of moving vortex 160 is around the central axis rotation of deciding vortex 150, but moving vortex 160 itself can not rotate around the central axis of self) to realize the compression of fluid.Be discharged to the high pressure side through the fluid of deciding after vortex 150 and moving vortex 160 compress by relief opening 152.In order to prevent that on high-tension side fluid is back to low voltage side via relief opening 152 under specific circumstances, be provided with one-way valve or outlet valve 170 at relief opening 152 places.
Fig. 2 shows the exploded perspective view of common a kind of outlet valve 170.As shown in Figure 2, outlet valve 170 comprise in the valve seat 172(valve seat 172 of ring roughly be provided with valve port 175), be arranged on the valve seat 172 with at least one valve block 174 of opening or closing valve port, prevent the valve guard 176 of valve block excessive deformation and the pin 179 that above-mentioned parts are fixed together.Outlet valve 170 with above-mentioned structure is seen Fig. 4 by retainer 178() 153(of hub section that is fixed on around the relief opening 152 of deciding vortex 150 sees Fig. 4) in.Fig. 3 A shows outlet valve 170 and is in closed condition, is in open mode and Fig. 3 B shows outlet valve 170.
In the outlet valve 170 of the routine shown in Fig. 2-4, because valve seat 172, valve guard 176 and retainer 178 are with respect to the certain positional relationship of the relief opening 152 of deciding vortex 150, the flow direction of fluid will carry out roughly turning to of 90 degree four times at the A shown in Fig. 4, B, C and D when the fluid after the compression is discharged to the high pressure side from relief opening 152.Particularly, because the upper surface of valve seat 172 is perpendicular to the valve port 175 on relief opening 152(or the valve seat 172) axial direction, when valve block 174 was opened, fluid had to carry out turn to (the position A place) of 90 degree roughly.Next, because the axial direction of flow channel in the valve guard 176 is roughly parallel to the axial direction of relief opening 152, so roughly the fluid that flows out from valve block 174 of along continuous straight runs has to again to carry out turn to (the position B) of 90 degree roughly.At last, the fluid that the flow channel along vertical direction roughly from valve guard 176 flows out is subject to the guiding of retainer 178 and trends towards flowing towards the zone of pressure minimum, and therefore, fluid also will carry out roughly turning to of 90 degree twice in the position of C and D roughly.These turn to the remarkable flow resistance that increases fluid.Therefore, produced obvious Pressure Drop to the high pressure side from relief opening 152.This Pressure Drop can cause the Efficiency Decreasing of compressor, and increases the energy consumption of compressor.
Therefore, need a kind of outlet valve that can effectively reduce flow resistance.
The model utility content
A purpose of one or more mode of executions of the present utility model provides a kind of outlet valve that can reduce flow resistance.
Another purpose of one or more mode of executions of the present utility model provides that a kind of cost is lower, the better simply outlet valve of structure.
Another purpose of one or more mode of executions of the present utility model provides the higher compressor of a kind of operational efficiency.
One or more to achieve these goals, according to aspect of the utility model, a kind of outlet valve is provided, comprise: valve body, the first end of described valve body is provided with fluid input, be provided with at least one fluid output that is communicated with described fluid input fluid and the valve block that is used to open or close described fluid output on the sidewall of wherein said valve body, the axial direction of wherein said fluid output tilts with respect to the axial direction of described fluid input.
Preferably, the angle between the axial direction of the axial direction of described fluid output and described fluid input is greater than 0 degree and less than or equal to 90 degree.
Preferably, the angle between the axial direction of the axial direction of described fluid output and described fluid input is more than or equal to 30 degree and less than or equal to 80 degree.
Preferably, the angle between the axial direction of the axial direction of described fluid output and described fluid input is more than or equal to 70 degree and less than or equal to 80 degree.
Preferably, the angle between the axial direction of the residing plane of described valve block and described fluid input is spent more than or equal to 0 degree and less than 90 when described valve block is closed described fluid output.
Preferably, the angle between the axial direction of the residing plane of described valve block and described fluid input is spent more than or equal to 10 degree and less than or equal to 60 when described valve block is closed described fluid output.
Preferably, the angle between the axial direction of the residing plane of described valve block and described fluid input is spent more than or equal to 10 degree and less than or equal to 20 when described valve block is closed described fluid output.
Preferably, described valve block with respect to the immovable point of described valve body between the described fluid output of being located axially at of described valve body and described fluid input.
Preferably, described outlet valve further comprises the valve guard be used to the displacement that limits described valve block.
Preferably, described valve guard with respect to the immovable point of described valve body between the described fluid output of being located axially at of described valve body and described fluid input.
Preferably, be provided with 2,3 or 4 described fluid outputs, and be provided with described valve block on each fluid output.
Preferably, described fluid output is arranged with the angle intervals Central Symmetry ground that equates around the axial direction of described fluid input.
Preferably, described fluid output is arranged in identical height along the axial direction of described fluid input.
Preferably, the second end of described valve body comprises piston.
Preferably, described outlet valve further comprises the sleeve that cooperates with described valve body, and described fluid output is positioned at the cavity of described sleeve.
Preferably, be formed with at least one opening on the sidewall of described sleeve.
Preferably, an end of described sleeve is formed with piston.
According to another aspect of the utility model, a kind of compressor is provided, comprise aforesaid outlet valve.
Preferably, described compressor is scroll compressor, and described scroll compressor comprises and decide vortex and moving vortex that the first end of the valve body of described outlet valve is fixed on described exhaust ports of deciding vortex.
Preferably, the first end of described valve body is by screw-thread fit or be fixed with pressure in described exhaust ports.
Preferably, described compressor comprises that further the valve body of described outlet valve consists of the part that described capacity is modulated mechanism for the capacity modulation mechanism of modulating compressor capacity by regulating the described axial displacement of deciding vortex.
Preferably, described capacity is modulated mechanism and is further comprised capacity modulation cylinder body, and the piston structure on the valve body of described outlet valve becomes and can move in described capacity modulation cylinder body.
Preferably, described compressor comprises that further the sleeve of described outlet valve consists of the part that described capacity is modulated mechanism for the capacity modulation mechanism of modulating compressor capacity by regulating the described axial displacement of deciding vortex.
Preferably, described capacity is modulated mechanism and is further comprised capacity modulation cylinder body, and the piston structure on the sleeve of described outlet valve becomes and can move in described capacity modulation cylinder body.
Preferably, described capacity modulation cylinder body is communicated with the external pressure source fluid by solenoid valve.
Preferably, described compressor is a kind of in scroll compressor, piston compressor, helical-lobe compressor, centrifugal compressor and the rotor compressor.
Be according to the outlet valve of one or more mode of executions of the present utility model and the advantage of compressor:
In the outlet valve according to a kind of mode of execution of the utility model, valve body comprises fluid input and at least one fluid output, and the axial direction of fluid output tilts with respect to the axial direction of fluid input.Compare with the outlet valve (shown in Fig. 2-4) that the axis of the fluid input of routine and fluid output is overlapping or parallel, the structure that tilts (the inclination here comprises the two orthogonal situation) with respect to the axial direction of fluid input according to the axial direction of this fluid output of the utility model mode of execution, because fluid its flow direction in flow process need not repeatedly to turn to the angle of 90 degree, so can reduce the flow resistance of fluid, thereby reduce the Pressure Drop that caused by outlet valve.On the other hand, owing to only be provided with fluid input and fluid output and be provided with valve block at fluid output at valve body, so can have very simple structure according to the outlet valve of the utility model mode of execution, therefore reduced manufacture cost.
In the outlet valve according to the further mode of execution of the utility model, angle between the axial direction of fluid output and the axial direction of fluid input can be greater than 0 degree and less than or equal to 90 degree, be preferably more than equal 30 the degree and less than or equal to 80 the degree, more preferably more than or equal to 70 the degree and less than or equal to 80 the degree.Perhaps, in other words, angle when valve block is closed fluid output between the axial direction of the residing plane of valve block and fluid input can more than or equal to 0 the degree and less than 90 the degree, be preferably more than equal 10 the degree and less than or equal to 60 the degree, more preferably more than or equal to 10 the degree and less than or equal to 20 the degree.The outlet valve that the angular range that adopts above-mentioned angular range particularly to be more preferably is constructed is compared with the conventional outlet valve shown in Fig. 2-4, and the raising that reduces the compressor operating efficient of bringing owing to flow resistance is significant.Through the reality test, the raising of compressor operating efficient can surpass 3% to 6% under different operating modes.
In the outlet valve according to the further mode of execution of the utility model, valve block with respect to the immovable point of valve body between fluid output and fluid input.In other words, valve block open that direction is arranged on can be so that on the minimized direction of the flow resistance of fluid.Thereby, can further reduce the flow resistance in the outlet valve.
In the outlet valve according to the further mode of execution of the utility model, outlet valve can further include the valve guard for the displacement of restriction valve block.Therefore, can reduce the possibility of valve block plastic deformation and the possibility of fatigue ruption, increase the reliability of outlet valve.In addition, also between fluid output and fluid input, namely valve guard can be fixed on the valve body in the position identical with valve block valve guard with respect to the immovable point of valve body.Thereby, reduced the increase of the flow resistance that the existence owing to valve guard brings.
In the outlet valve according to the further mode of execution of the utility model, the first end of valve body can or be fixed with pressure in the exhaust ports of the compressing mechanism of described compressor by screw-thread fit.Because valve body can directly be fixed to exhaust ports, be used for the fixedly retainer of the conventional outlet valve shown in Fig. 2-4 so saved, and therefore further reduced because the increase of the flow resistance that retainer causes.
In the outlet valve according to the further mode of execution of the utility model, 2,3 or 4 fluid outputs can be set, and on each fluid output, be provided with described valve block.Further, these fluid outputs can be arranged with the angle intervals Central Symmetry ground that equates around the axial direction of fluid input.In addition, these fluid outputs can also be arranged in along the axial direction of fluid input identical height.Adopt this structure, can increase total cross-section area of fluid output further to avoid Pressure Drop.In addition, because being arranged symmetrically with of fluid output can more effectively realize on high-tension side pressure balance, reduce noise and pressure surge, guarantee more runs steadily of compressor.
In the compressor according to the utility model mode of execution, owing to adopted above-mentioned outlet valve, so can have the above-mentioned advantage of being brought by outlet valve.
In the compressor according to the further mode of execution of the utility model, compressor can be scroll compressor, and scroll compressor can comprise and decide vortex and moving vortex that outlet valve is fixed on the exhaust ports of deciding vortex.Particularly, when compressor is the compressor of volume-variable, compressor may further include for the capacity modulation mechanism of modulating compressor capacity by regulating the axial displacement of deciding vortex, and the valve body of outlet valve or the sleeve that cooperates with valve body can the formation capacity be modulated the part of mechanism.More specifically, capacity modulation mechanism can comprise capacity modulation cylinder body, and the second end of the valve body of outlet valve or the sleeve of outlet valve can comprise the piston that can move in capacity is modulated cylinder body.Because the first end of valve body is fixedly connected with the relief opening of deciding vortex, piston on the second end of valve body or the piston on the sleeve can be modulated axially motion in the cylinder body at capacity, thereby therefore can decide the capacity modulation function that voraxial moves to realize compressor so that exhaust valve spindle drives to motion by the pressure in the control capacity modulation cylinder body.Because the member (for example piston) of outlet valve and control compressor capacity is configured to one, has not only reduced number of components but also simplified the assembly technology of compressor, thereby reduced the manufacture cost of compressor.
In the compressor according to the further mode of execution of the utility model, compressor can be a kind of in scroll compressor, piston compressor, helical-lobe compressor, centrifugal compressor and the rotor compressor.In other words, can be applied to various compressors according to the outlet valve of the utility model mode of execution, have good versatility.
Description of drawings
By the description referring to accompanying drawing, it is easier to understand that the feature and advantage of one or several mode of execution of the present utility model will become, wherein:
Fig. 1 is the longitudinal section of the scroll compressor of routine;
Fig. 2 is the stereogram of the conventional outlet valve among Fig. 1;
Fig. 3 A and 3B are respectively the schematic representation that outlet valve shown in Figure 2 is in closed condition and open mode;
Fig. 4 is near the enlarged view of the relief opening of deciding vortex that scroll compressor shown in Figure 1 is shown;
Fig. 5 shows the scroll compressor longitudinal section according to a kind of mode of execution of the utility model;
Fig. 6 shows the stereogram according to the outlet valve of the utility model the first mode of execution;
Fig. 7 shows the sectional view according to the outlet valve of the utility model the first mode of execution;
Fig. 8 A and 8B are respectively plan view and the worm's eye views according to the outlet valve of the utility model the second mode of execution;
Fig. 9 A and 9B are respectively plan view and the worm's eye views according to the outlet valve of the utility model the 3rd mode of execution;
Figure 10 A and 10B are respectively exploded perspective view and the assembling stereograms according to the outlet valve of the utility model the 4th mode of execution; And
Figure 11 is the longitudinal section according to the outlet valve of the utility model the 5th mode of execution.
Embodiment
Following description related to the preferred embodiment only is exemplary, and never is the restriction to the utility model and application or usage.
The essential structure of conventional scroll compressor 1 and running are described referring to Fig. 1-4 in the background technique part.Fig. 5 shows the scroll compressor 100A according to the utility model mode of execution.Adopted various outlet valve 10A, 10B, 10C and the 10D shown in Fig. 6-10B to replace the conventional outlet valve 170 shown in Fig. 1 at scroll compressor 100A of the present utility model.Particularly, in Fig. 5, adopt with Fig. 1 in identical reference character represent parts same as shown in Figure 1, the structure of these parts will no longer repeat.
As shown in Figure 5, the scroll compressor 100A according to the utility model mode of execution comprise housing 110, be arranged on housing 110 1 ends top cover 112, be arranged on the bottom 114 of housing 110 the other ends and be arranged on top cover 112 and housing 110 between be separated into the dividing plate 116 of high pressure side and low voltage side with the inner space with compressor.Consist of the high pressure side between dividing plate 116 and the top cover 112, and consist of low voltage side between dividing plate 116, housing 110 and the bottom 114.Be provided with for the air input joint 118 that sucks fluid in low voltage side, be provided with the exhaust joint 119 for the fluid after discharging compression in the high pressure side.
Be provided with the outlet valve 10A according to the utility model the first mode of execution at relief opening 152 places that decide vortex 150.Shown in Fig. 6 and 7, outlet valve 10A can comprise: valve body 12, the first end 14 of described valve body 12 can be fixed (for example be threaded connection or be fixed with pressure) at the relief opening of deciding vortex 150 152 places of compressor 100A, and the first end of described valve body 12 is provided with the fluid input 15 that aligns with relief opening 152.The quantity that is provided with at least one the fluid output 17(fluid output 17 in the example shown in Fig. 6 and 7 that is communicated with fluid input 15 fluids on the sidewall of valve body 12 is 2) and be used to open or close fluid output valve block 20.In the example shown in Fig. 6 and 7, valve block 20 can be two, but it should be appreciated by those skilled in the art that the quantity of valve block 20 also can be 1 or more.Particularly, as shown in Figure 7, the axial direction X2 of each fluid output 17 tilts with respect to the axial direction X1 of fluid input 15.Residing plane X 3 was off plumbs when in other words, the axial direction X1 of fluid input 15 and valve block 20 were closed fluid output 17.
Overlapping or parallel (perhaps in other words with the axis of fluid output (they can regard that the bottom by the valve port 175 on the valve seat 172 consists of respectively with top as) with the fluid input shown in Fig. 2-4, the axial direction of fluid input is vertical with plane, valve block 174 place) outlet valve 170 compare, (residing plane X 3 was off plumbs when perhaps in other words, the axial direction X1 of fluid input 15 and valve block 20 were closed fluid output 17) of tilting according to the axial direction X2 of the fluid output 17 of the outlet valve 10A of the utility model mode of execution with respect to the axial direction X1 of fluid input 15.Therefore, enter the valve body 12 to fluid from fluid output 17 from fluid input 15 at fluid and discharge the process of valve bodies 12 via valve block 20, the flow direction of fluid is not that the mode with right angle (90 degree) turns to.Therefore, the flow resistance of outlet valve 10A can be reduced, thereby can reduce the Pressure Drop that is caused by outlet valve.
In the preferred exemplary shown in Fig. 6-7, the angle [alpha] between the axial direction X2 of fluid output 17 and the axial direction X1 of fluid input 15 is set for more than or equal to 70 degree and less than or equal to 80 degree.Perhaps, the angle beta between the axial direction X1 of valve block 20 residing plane X 3 and fluid input 15 is set for more than or equal to 10 degree and less than or equal to 20 degree when valve block 20 is closed fluid output 17.
Can also comprise valve guard 22 for the displacement of restriction valve block 20 according to the outlet valve 10A of the utility model the first mode of execution.Valve block 20 and valve guard 22 can be fixed on the valve body 12 by the fastening piece such as screw 24.In addition, for the ease of assembling and prevent that valve block or valve guard from around screw 24 rotations, can also adopt pin 26 also to realize further location.
Particularly, the immovable point with respect to valve body 12 of valve block 20 (for example, the position of screw 24) can be arranged in being located axially between fluid output 17 and the fluid input 15 of described valve body.In other words, valve block 20 open that direction is arranged on can be so that on the minimized direction of the flow resistance of fluid.This structure can further reduce the flow resistance among the outlet valve 10A.Further, valve guard 22 also can be arranged in being located axially between fluid output 17 and the fluid input 15 of described valve body with respect to the immovable point (for example, the position of screw 24) of valve body 12.
The inventor to of the present utility model shown in Fig. 6-7 outlet valve and outlet valve shown in Figure 2 carried out contrast test.The result is as shown in table 1.
The inventor has done two groups of tests (referring to test sequence number 3-4) to done four groups of tests (referring to test sequence number 1-2 and 5-6) under different operating modes according to outlet valve of the present utility model to conventional outlet valve shown in Figure 2 under different operating modes.Adopt the power consumpiton of the cold/compressor of EER(=compressor) represent the operational efficiency of compressor.With the EER of the compressor that is provided with conventional outlet valve shown in Figure 2 as benchmark, the compressor of the with good grounds outlet valve of the present utility model of calculating and setting and the EER of compressor of the outlet valve of any type is not set.The result shows, inhalation temperature and delivery temperature at compressor are respectively in the situation of 45 ℉ and 130 ℉, adopt the EER of the compressor of outlet valve of the present utility model to improve 3.84% to 4.08%, and be respectively in the situation of 45 ℉ and 100 ℉ in inhalation temperature and the delivery temperature of compressor, adopt the EER of the compressor of outlet valve of the present utility model to improve 6.69% to 7.01%.
In order to verify the reliability of above-mentioned test, the inventor has also done two groups of tests (referring to test sequence number 7-8) to the compressor that any outlet valve is not set.Test result shows, compares with the situation that conventional outlet valve is set, and the EER that does not arrange in the situation of any outlet valve has improved respectively 4.08% and 7.94%.
According to the above results, the operational efficiency that obviously is provided with according to the compressor of outlet valve of the present utility model is significantly higher than the compressor that is provided with conventional outlet valve, and only a shade below the operational efficiency of the compressor that outlet valve is not set.Consider that outlet valve must be set under many circumstances to flow backwards to prevent high-pressure liquid, so the effect that outlet valve of the present utility model brings is very significant with respect to conventional outlet valve and has surpassed those skilled in the art's expection.
In addition, as shown in Figure 5, can be a kind of compressor of volume-variable according to the scroll compressor 100A of the utility model mode of execution.Therefore, scroll compressor 100A further comprises capacity modulation mechanism 180.The capacity of compressor is modulated by capacity modulation mechanism 180 by regulating the axial displacement (namely deciding the axial distance between vortex 150 and the moving vortex 160) of deciding vortex 150.
Simultaneously referring to shown in Fig. 6 and 7, the part that the valve body 12 of outlet valve 10A can formation capacity modulation mechanism 180.Particularly, capacity modulation mechanism 180 further comprises capacity modulation cylinder body 182, and the second end 16 of the valve body 12 of outlet valve 10A can comprise can modulate at capacity the piston 18 of cylinder body 182 interior motions.Capacity modulation cylinder body 182 is communicated with the external pressure source fluid via connecting tube 184.Solenoid valve can be set with the pressure in the control capacity modulation cylinder body 182 in the pipeline of connecting tube 184.
In real-world operation, when needs reduced the capacity of scroll compressor 100A, the solenoid valve in the pipeline of control connection pipe 184 was with the pressure in the reduction capacity modulation cylinder body 182, thereby the piston 18 of the second end 16 of outlet valve 10A will move upward.Because the first end 14 of outlet valve 10A is fixedly connected with the relief opening 152 of deciding vortex 150, therefore thereby deciding vortex 150 will upwards be mentioned at the end plate 164 of the helical blade 156 of deciding vortex 150 and moving vortex 160 and move the helical blade 166 of vortex 160 and deciding and be formed the gap between the end plate 154 of vortex 150, the Partial shrinkage fluid will be from this clearance leakage to low voltage side, thereby reduces the capacity of compressor.On the contrary, when needs increased the capacity of scroll compressor 100A, the solenoid valve in the pipeline of control connection pipe 184 was with the pressure in the increase capacity modulation cylinder body 182, thereby the piston 18 of the second end 16 of outlet valve 10A will move downward.To be pressed downward closed gap of deciding between vortex 150 and the moving vortex 160 thereby therefore decide vortex 150, thereby increase the capacity of compressor.
Fig. 8 A and 8B are respectively plan view and the worm's eye views according to the outlet valve 10B of the utility model the second mode of execution.Different from the first mode of execution of the present utility model, in the outlet valve 10B of the second mode of execution of the present utility model, be provided with three fluid outputs 17 and three groups of valve blocks 20 and valve guard 22.In addition, these fluid outputs 17 can be arranged with the angle intervals Central Symmetry ground that equates around the axial direction of fluid input 15.In addition, these described fluid outputs 17 can be arranged in along the axial direction of fluid input 15 identical height.
Fig. 9 A and 9B are respectively plan view and the worm's eye views according to the outlet valve 10C of the utility model the 3rd mode of execution.Different from the first mode of execution of the present utility model, in the outlet valve 10C of the 3rd mode of execution of the present utility model, be provided with four fluid outputs 17 and four groups of valve blocks 20 and valve guard 22.In addition, these fluid outputs 17 can be arranged with the angle intervals Central Symmetry ground that equates around the axial direction of fluid input 15.In addition, these described fluid outputs 17 can be arranged in along the axial direction of fluid input 15 identical height.
Figure 10 A and 10B are respectively exploded perspective view and the assembling stereograms according to the outlet valve 10D of the utility model the 4th mode of execution.Different from above-mentioned first, second, and third mode of execution of the present utility model, be not provided for the piston of capacity modulation according to the outlet valve 10D of the utility model the 4th mode of execution, so structure is more simple and can be used for the fixing scroll compressor of capacity or the scroll compressor adjusted of realization capacity otherwise.
Figure 11 shows the outlet valve 10E according to the 5th mode of execution of the present utility model.The valve body 12 of outlet valve 10E shown in Figure 11, fluid input 15, structure and the mode of execution shown in relation and Figure 10 A-10B of fluid output 17, valve block 20 etc. are similar, do not repeat them here.Special needs to be pointed out is that the valve block 20 shown in Figure 11 is in open mode.Yet different from the 4th mode of execution is, outlet valve 10E further comprises the sleeve 30 that cooperates with valve body 12, and fluid output 17 is positioned at the cavity of sleeve 30.Sleeve 30 such as can be by press fit, be threaded, the mode such as welding and valve body 12 be fixed together.Can form at least one opening 32 on the sidewall of sleeve 30.One end of sleeve 30 can form piston 18.Outlet valve 10E shown in Figure 11 also can be applied in the scroll compressor with capacity modulation function shown in Figure 5.More specifically, sleeve 30 or valve body 12 can be fixed on relief opening 152 places that decide vortex 150, and the piston 18 on the sleeve 30 can be engaged in the capacity modulation cylinder body 182.In like manner, adopted the scroll compressor of the outlet valve 10E of this mode of execution to have carried out the capacity modulation in aforesaid mode.
In the above-mentioned preferred implementation, provided angle [alpha] and set for more than or equal to 70 degree and less than or equal to the example of 80 degree (perhaps angle beta is set for more than or equal to 10 degree and less than or equal to 20 degree).But, it should be appreciated by those skilled in the art that the utility model is not limited to this, but the scope of above-mentioned angle [alpha] and β can also be chosen other and is worth to realize to compare with above-mentioned preferable range the slightly poor effect that still is higher than conventional outlet valve.For example, the angle [alpha] between the axial direction X1 of the axial direction X2 of fluid output 17 and fluid input 15 can be more than or equal to 30 degree and less than or equal to 80 degree.Perhaps in other words, the angle beta between the axial direction X of valve block 20 residing plane X 3 and fluid input 15 can be more than or equal to 10 degree and less than or equal to 60 degree when valve block 20 is closed fluid output 17.
Further, the angle [alpha] between the axial direction X1 of the axial direction X2 of fluid output 17 and fluid input 15 can be greater than 0 degree and less than or equal to 90 degree.Perhaps in other words, the angle beta between the axial direction X1 of valve block 20 residing plane X 3 and fluid input 15 can be more than or equal to 0 degree and less than 90 degree when valve block 20 is closed fluid output 17.
Although fluid input and fluid output are depicted as circle in the above-mentioned mode of execution that describes with reference to the accompanying drawings, it should be appreciated by those skilled in the art that fluid input and fluid output can have other any shapes except circle.
Similar with the first mode of execution, shown in Fig. 8 A-11 second, third, in the 4th and the 5th mode of execution, valve block can be single valve block, also can 2 or a plurality of stacked valve blocks.In addition, similar with the second and the 3rd mode of execution shown in Fig. 8 A-9B, Figure 10 A-10B and the 4th and the 5th mode of execution shown in Figure 11 also can be retrofit into and comprise a plurality of fluid outputs.
In addition, the effect of the outlet valve of the utility model mode of execution has been described with reference to scroll compressor, but those skilled in the art should understand that, outlet valve of the present utility model can also be applied to the compressor of other types, include but not limited to piston compressor, helical-lobe compressor, centrifugal compressor and rotor compressor, to realize reducing the Pressure Drop that is caused by outlet valve and the effect that increases the operational efficiency of compressor.In addition, those skilled in the art should understand that outlet valve of the present utility model can also be applied to the machinery that other need convection cell to discharge to control, such as pump etc.
Although described various mode of execution of the present utility model in detail at this, but should be appreciated that the utility model is not limited to the embodiment of describing in detail and illustrating here, in the situation that does not depart from essence of the present utility model and scope, can be realized by those skilled in the art other modification and variant.All these modification and variant all fall in the scope of the present utility model.And all members described here can be replaced by the member that is equal on the other technologies.
Claims (26)
1. an outlet valve (10A, 10B, 10C, 10D, 10E) comprising:
Valve body (12), the first end (14) of described valve body (12) is provided with fluid input (15),
It is characterized in that: be provided with at least one fluid output (17) that is communicated with described fluid input (15) fluid and the valve block (20) that is used to open or close described fluid output on the sidewall of described valve body (12),
It is characterized in that the axial direction of described fluid output (17) is with respect to the axial direction inclination of described fluid input (15).
2. outlet valve as claimed in claim 1, the angle between the axial direction of the axial direction of wherein said fluid output (17) and described fluid input (15) is greater than 0 degree and less than or equal to 90 degree.
3. outlet valve as claimed in claim 2, the angle between the axial direction of the axial direction of wherein said fluid output (17) and described fluid input (15) is more than or equal to 30 degree and less than or equal to 80 degree.
4. outlet valve as claimed in claim 3, the angle between the axial direction of the axial direction of wherein said fluid output (17) and described fluid input (15) is more than or equal to 70 degree and less than or equal to 80 degree.
5. outlet valve as claimed in claim 1, wherein when described valve block (20) is closed described fluid output (17) angle between the axial direction of the residing plane of described valve block (20) and described fluid input (15) more than or equal to 0 degree and less than 90 degree.
6. outlet valve as claimed in claim 5, wherein when described valve block (20) is closed described fluid output (17) angle between the axial direction of the residing plane of described valve block (20) and described fluid input (15) more than or equal to 10 degree and less than or equal to 60 degree.
7. outlet valve as claimed in claim 6, wherein when described valve block (20) is closed described fluid output (17) angle between the axial direction of the residing plane of described valve block (20) and described fluid input (15) more than or equal to 10 degree and less than or equal to 20 degree.
8. such as each described outlet valve among the claim 1-7, wherein said valve block (20) with respect to the immovable point of described valve body (12) between the described fluid output of being located axially at of described valve body (17) and described fluid input (15).
9. outlet valve as claimed in claim 8, wherein this outlet valve further comprises be used to the valve guard (22) that limits described valve block (20) displacement.
10. outlet valve as claimed in claim 9, wherein said valve guard (22) with respect to the immovable point of described valve body (12) between the described fluid output of being located axially at of described valve body (17) and described fluid input (15).
11. such as each described outlet valve among the claim 1-7, wherein be provided with 2,3 or 4 described fluid outputs (17), and be provided with described valve block (20) on each fluid output (17).
12. outlet valve as claimed in claim 11, wherein said fluid output (17) is arranged with the angle intervals Central Symmetry ground that equates around the axial direction of described fluid input (15).
13. outlet valve as claimed in claim 11, wherein said fluid output (17) is arranged in identical height along the axial direction of described fluid input (15).
14. such as each described outlet valve among the claim 1-7, second end (16) of wherein said valve body (12) comprises piston (18).
15. such as each described outlet valve among the claim 1-7, further comprise the sleeve (30) that cooperates with described valve body (12), described fluid output (17) is positioned at the cavity of described sleeve (30).
16. outlet valve as claimed in claim 15 is formed with at least one opening (32) on the sidewall of wherein said sleeve (30).
17. outlet valve as claimed in claim 15, an end of wherein said sleeve (30) is formed with piston (18).
18. a compressor (100A) is characterized in that comprising such as each described outlet valve (10A, 10B, 10C, 10D, 10E) among the claim 1-17.
19. compressor as claimed in claim 18, wherein said compressor is scroll compressor, and described scroll compressor comprises decides vortex (150) and moving vortex (160), and the first end of the valve body of described outlet valve (14) is fixed on the described relief opening (152) of deciding vortex (150) and locates.
20. compressor as claimed in claim 19, the first end (14) of wherein said valve body (12) are by screw-thread fit or be fixed with pressure and locate at described relief opening (152).
21. compressor as claimed in claim 19, comprise that further the valve body of described outlet valve (12) consists of the part of described capacity modulation mechanism (180) for the capacity modulation mechanism (180) of modulating compressor capacity by regulating the described axial displacement of deciding vortex (150).
22. compressor as claimed in claim 21, wherein said capacity modulation mechanism (180) further comprises capacity modulation cylinder body (182), and the piston (18) on the valve body of described outlet valve (12) is constructed to be permeable to motion in described capacity modulation cylinder body (182).
23. compressor as claimed in claim 19, comprise that further the sleeve of described outlet valve (30) consists of the part of described capacity modulation mechanism (180) for the capacity modulation mechanism (180) of modulating compressor capacity by regulating the described axial displacement of deciding vortex (150).
24. compressor as claimed in claim 23, wherein said capacity modulation mechanism (180) further comprises capacity modulation cylinder body (182), and the piston (18) on the sleeve of described outlet valve (30) is constructed to be permeable to motion in described capacity modulation cylinder body (182).
25. such as claim 22 or 24 described compressors, wherein said capacity modulation cylinder body (182) is communicated with the external pressure source fluid by solenoid valve.
26. compressor as claimed in claim 18, wherein said compressor are a kind of in scroll compressor, piston compressor, helical-lobe compressor, centrifugal compressor and the rotor compressor.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220470547 CN202789552U (en) | 2012-09-14 | 2012-09-14 | Discharge valve and compressor comprising same |
| PCT/CN2013/078898 WO2014040449A1 (en) | 2012-09-14 | 2013-07-05 | Exhaust valve and compressor comprising same |
| US14/427,128 US9926932B2 (en) | 2012-09-14 | 2013-07-05 | Discharge valve and compressor comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220470547 CN202789552U (en) | 2012-09-14 | 2012-09-14 | Discharge valve and compressor comprising same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202789552U true CN202789552U (en) | 2013-03-13 |
Family
ID=47816822
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220470547 Expired - Fee Related CN202789552U (en) | 2012-09-14 | 2012-09-14 | Discharge valve and compressor comprising same |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202789552U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014040449A1 (en) * | 2012-09-14 | 2014-03-20 | 艾默生环境优化技术(苏州)有限公司 | Exhaust valve and compressor comprising same |
| CN103671125A (en) * | 2012-09-14 | 2014-03-26 | 艾默生环境优化技术(苏州)有限公司 | Discharge valve and compressor comprising same |
-
2012
- 2012-09-14 CN CN 201220470547 patent/CN202789552U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014040449A1 (en) * | 2012-09-14 | 2014-03-20 | 艾默生环境优化技术(苏州)有限公司 | Exhaust valve and compressor comprising same |
| CN103671125A (en) * | 2012-09-14 | 2014-03-26 | 艾默生环境优化技术(苏州)有限公司 | Discharge valve and compressor comprising same |
| CN103671125B (en) * | 2012-09-14 | 2016-03-30 | 艾默生环境优化技术(苏州)有限公司 | Discharge valve and compressor comprising same |
| US9926932B2 (en) | 2012-09-14 | 2018-03-27 | Emerson Climate Technologies (Suzhou) Co., Ltd. | Discharge valve and compressor comprising same |
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Granted publication date: 20130313 Termination date: 20170914 |