CN1566708A - Overcompression prevention device for tubine compressor - Google Patents
Overcompression prevention device for tubine compressor Download PDFInfo
- Publication number
- CN1566708A CN1566708A CN 03137779 CN03137779A CN1566708A CN 1566708 A CN1566708 A CN 1566708A CN 03137779 CN03137779 CN 03137779 CN 03137779 A CN03137779 A CN 03137779A CN 1566708 A CN1566708 A CN 1566708A
- Authority
- CN
- China
- Prior art keywords
- exhaust
- valve
- chamber
- passage
- channel
- 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.)
- Granted
Links
Images
Abstract
The invention is about an over-compression preventing device of scroll compressor, which comprises: an air exhaust adjusting valve inserted from inside, sliding to the shaft direction with the pressure difference between the compressing chamber and the outlet chamber capable of opening or closing the outlet holes; and a valve stopper combined on the end of the outlet holes for controlling the sliding of the air exhaust adjusting valve; the invention embeds the air exhaust adjusting valve into the outlet hole, improved the combination of the air exhaust adjusting valve and the production of compressor, reduced the volume of the compressor, and improved the efficiency and reliability of the compressor.
Description
Technical field
The present invention relates to a kind of anti-overcompression device of turbocompressor of compressor field, particularly relate to a kind of handling safety, modularity is outstanding, and can reduce the anti-overcompression device of the turbocompressor of volume.
Background technique
Usually, turbocompressor is moved a plurality of turbines relatively, and continuous mobile pressing chamber sucks freezing mixture, compress, the final discharge.Because of turbocompressor has the outstanding performance of high volumetric efficiency than the compressor of other types, thereby be widely used as compressor for cooling fluid.The discharge elapsed time of this turbocompressor is depended on the geometrical configuration of turbine lap, and therefore the suction volume of the turbine of the shape that formalizes and the ratio of displaced volume are fixed, and this fixed volume ratio determines its pressure ratio.
The intrinsic design pressure of pressing and discharging pressure ratio and turbocompressor between pressing when suction that operating conditions determined is than consistent the time, and compression loss is a minimum; But when these two pressure ratios were inconsistent, compression loss will increase greatly.Just, when design pressure than be higher than operating pressure than the time, even reaching to discharge, the gas pressure in the pressing chamber do not press, as long as to discharging the elapsed time, gas in the compression process will drain to exhaust port, at this moment high the causing from discharging the adverse current phenomenon of chamber to pressing chamber of gas pressure because of discharging the chamber.
On the contrary, when design pressure than be lower than operating pressure than the time, even the gas pressure in the pressing chamber is consistent with head pressure, if but also be less than and discharge the elapsed time, continue to cause overcompression and lose phenomenon because of compressing.Thereby, in order to prevent phenomenon because of design pressure compares and operating pressure increases than the inconsistent compression loss that causes, usually at operating pressure than when being lower than the design pressure ratio, the drain tap device is set, if press, just the gas in the pressing chamber is discharged in advance and discharges the chamber so that the gas in the compression process has reached to discharge.
Fig. 1 is the part sectioned view of general turbocompressor, and Fig. 2 is the amplification profile of existing drain tap device.
As shown in Figure 1, 2, existing turbocompressor includes as the bottom: the shell 1 with gas suction pipe SP and gas outlet pipe DP; Be fixed on the main frame 2 and the auxiliary frame (not shown) of the both sides up and down of shell 1 inner peripheral surface; Be installed in the drive motor 3 between main frame 2 and the auxiliary frame (not shown); Be embedded in the center of drive motor 3, and pass the live axle 4 that main frame 2 is passed on the rotating force of drive motor 3; Combine with live axle 4, and be installed in the rotary turbine 5 of main frame 2 upper ends; Be combined in rotary turbine 5, and for forming the fixed turbine 6 that a plurality of pressing chambers are fixed on main frame 2 upper ends; Be combined in the back side of fixed turbine 6, offset the discharge noise of the gas discharged, and be suction chamber S1 and the high low pressure demarcation strip 7 of discharging chamber S2 the internal separation of shell 1; Be combined in the back side of the lightweight plate portion of fixed turbine 6, and prevent to discharge the valve for preventing reverse-flow door assembly 8 of the adverse current of gas.
Shape with involute on rotary turbine 5 and fixed turbine 6 has respectively formed lap 5a, the 6a that engages one another and form a plurality of pressing chamber P in pairs, has embedded the closed chamber material (not shown) that pressurized gas leaks outside that prevents that can move up and down again at the vertical surface of its lap 5a, 6a.
In addition, formed suction port 6b, near central authorities, formed exhaust port 6c, and formed the exhaust port 6d that is communicated to discharge chamber S2 from middle pressing chamber P in the both sides of its exhaust port 6c in the outmost lap outside that is positioned at fixed turbine 6.
The not end of exhaust port 6d installed as shown in Figure 2 along with pressing chamber P and discharge pressure difference between the S2 of chamber, open or close the guiding type exhaust of exhaust port 6d and adjust valve 9A.Adjust the rear side of valve 9A in exhaust, the fixture 9B that its exhaust of control is adjusted the opening degree of valve 9A adjusts valve with screw 9C with exhaust and connects together and be installed on the fixed turbine 6.
Mark 0 among the figure is the anti-rotation accessory open loop damping ring (oldham) of rotary turbine.
Now the working condition with aforesaid existing turbocompressor is described as follows.
Live axle 4 rotates with drive motor 3 because of additional power source, thereupon, rotary turbine 5 rotates to the position that is equivalent to eccentric distance, meanwhile between lap 5a, the 6a of rotary turbine 5 and fixed turbine 6, form a plurality of pressing chamber P in couples, this pressing chamber P is again along with the continuous rotating motion of rotary turbine 5 is moved to the center, and carries out the process that reduces to absorb, compress and discharge coolant gas because of volume repeatedly.
At this moment, as mentioned above, when design pressure than with operating pressure than consistent the time, coolant gas flow into outmost pressing chamber P by the suction port 6b of fixed turbine 6, afterwards more gradually inside last pressing chamber P move and be compressed, thereby normally discharged by discharging chamber 6c.On the contrary, when design pressure than be lower than operating pressure than the time, just the pressing chamber P of a part of pressurized gas in the centre that moves toward last pressing chamber P opens exhaust by exhaust port 6d and adjusts valve 9A, and is discharged to discharge chamber S2 in advance, thereby prevented the overcompression phenomenon of pressurized gas in advance.
But, on the drain tap device of above-mentioned existing turbocompressor, because exhaust is adjusted valve 9A and is set to the guiding type valve, so when connecting this exhaust adjustment valve 9A with screw 9C, because of fastening strength, valve 9A is that the center rotates with screw 9C, break away to the center that makes exhaust port 6d and exhaust adjust valve 9A, therefore not only do not reach its intended purposes, but also the bad problem of the performance that can cause compressor, therefore also need carefully to assemble, thereby caused a lot of troubles, cause manufacturing efficiency low to packing engineering.
And, from the characteristics of guiding valve, be arranged on the not end of exhaust port 6d, thereby to the smaller volume that makes exhaust port 6d, thereby cause the efficient of compressor to reduce.
This shows that the anti-overcompression device of above-mentioned existing turbocompressor still has many defectives, and demands urgently further being improved.
In order to solve the defective that existing turbocompressor exists, relevant manufacturer there's no one who doesn't or isn't seeks solution painstakingly, but do not see always that for a long time suitable design finished by development, therefore how to found a kind of turbocompressor that has that volume is little, cost is low concurrently and can have comprehensive adjustment function when using, just become the current industry utmost point to need improved target.
Because the defective that above-mentioned existing turbocompressor exists, the inventor is actively studied innovation, through constantly studying, designing based on abundant practical experience and professional knowledge, and after studying sample and improvement repeatedly, create the present invention who has practical value finally.
Summary of the invention
Main purpose of the present invention is, overcome the defective that above-mentioned existing turbocompressor exists, and provide a kind of anti-overcompression device of turbocompressor of new structure, technical problem underlying to be solved is to make it can correctly open or close the exhaust of closing exhaust port to adjust valve, thereby packing engineering is become easily, can improve the reliability and the industrial production of compressor.
Another object of the present invention is to, a kind of anti-overcompression device that can reduce the turbocompressor of the volume that produces because of exhaust port is provided.
Purpose of the present invention and to solve its technical problem underlying be to adopt following technological scheme to realize.The anti-overcompression device of the aforesaid turbocompressor that proposes according to the present invention, it comprises fixed turbine and is engaged in the rotary turbine that rotatablely moves on the said fixing turbine and form the pressing chamber that moves continuously, and comprise when the operating pressure ratio between suction pressure and the discharge pressure is higher than the design pressure ratio, for being rejected in advance, a part of pressurized gas before will discharging discharges the chamber, thereby prevent the overcompression phenomenon, with the fluid passage is benchmark, exhaust port the place ahead at fixed turbine or rotary turbine is provided with exhaust port, it also comprises the inside insertion from exhaust port, along with the pressure difference between pressing chamber and the discharge chamber, axially carry out smooth motion, and have the exhaust adjustment valve of the effect of opening or closing above-mentioned exhaust port; And the valve actuator that is combined in above-mentioned exhaust port end for the sliding movement setting of control exhaust adjustment valve.
The object of the invention to solve the technical problems can also be further achieved by the following technical measures.
The anti-overcompression device of aforesaid turbocompressor, wherein said exhaust port comprise from pressing chamber gets through the first passage of formation to discharging the chamber; Extend and form from the end of first passage, and portion embeds the second channel that valve is adjusted in above-mentioned exhaust within it; Get through formation from the side of second channel to discharging the chamber, and when high-pressure ratio is moved, have the third channel that is communicated with first passage more than 1 at least.
The anti-overcompression device of aforesaid turbocompressor, the boundary face of wherein said first passage and second channel is scalariform.
The anti-overcompression device of aforesaid turbocompressor, wherein said exhaust are adjusted valve and are provided with spherical in shape.
The anti-overcompression device of aforesaid turbocompressor, wherein said exhaust are adjusted the valve setting and are clavate.
The anti-overcompression device of aforesaid turbocompressor, the boundary face setting of wherein said first passage and second channel is the internal conical surface shape, and adjusts the valve setting with the exhaust on the boundary boundary that face connects of first passage and second channel and be corresponding therewith outer conical surface shape.
The anti-overcompression device of aforesaid turbocompressor, the middle body hollow of wherein said valve actuator forms when compressor normally moves, make the pressurized gas of discharging the chamber flow into second channel, and the direction pressurization of valve to first passage adjusted in exhaust; On the contrary, when moving, can discharge the four-way of the fluid at the pressure back side that remains in exhaust adjustment valve with high-pressure ratio.
The anti-overcompression device of aforesaid turbocompressor, the inside of the relative valve actuator of valve is adjusted in wherein said exhaust, also is provided with to alleviate the collision that takes place when valve opening is adjusted in exhaust, plays the buffer unit of buffer function.
The present invention compared with prior art has tangible advantage and beneficial effect.By above technological scheme as can be known, provided by the invention have fixed turbine and be engaged in the rotary turbine that rotatablely moves on this fixed turbine and form the pressing chamber that moves continuously, and when the operating pressure ratio between suction pressure and the discharge pressure is higher than the design pressure ratio, for being rejected in advance, a part of pressurized gas before will discharging discharges the chamber, thereby prevent the overcompression phenomenon, when being benchmark, set up the turbocompressor of exhaust port in exhaust port the place ahead of fixed turbine or rotary turbine with the fluid passage.Anti-overcompression device according to the present invention includes as the bottom: insert from the inside of exhaust port, along with the pressure difference between pressing chamber and the discharge chamber, axially carry out sliding movement, and have out or close the exhaust adjustment valve of the effect of above-mentioned exhaust port; Adjust the not valve actuator of end that is combined in above-mentioned exhaust port that the sliding movement of valve designs for controlling exhaust.
Anti-overcompression device according to turbocompressor of the present invention, valve is adjusted in exhaust to be embedded in the exhaust port, adjust the modularity of valve and the producibility and the reliability of compressor thereby improved exhaust, reduced the volume of compressor, improved the efficient of compressor.
In sum, the anti-overcompression device of the turbocompressor of special construction of the present invention, can correctly open or close the exhaust of closing exhaust port and adjust valve, make packing engineering become easy, thereby can improve the reliability and the industrial production of compressor, be a kind of anti-overcompression device that can reduce the turbocompressor of the volume that produces because of exhaust port.It has above-mentioned many advantages and use value, no matter it structurally or bigger improvement all arranged on the function, have large improvement technically, and produced handy and practical effect, and has the effect of enhancement really, thereby being suitable for practicality more, and not seeing have similar structural design to publish or use in like product, really is a new and innovative, progressive, practical new design.
Above-mentioned explanation only is the general introduction of technical solution of the present invention, for can clearer understanding technological means of the present invention, and can be implemented according to the content of specification, below with preferred embodiment of the present invention and conjunction with figs. describe in detail as after.
Description of drawings
Fig. 1 is the part sectioned view of existing turbocompressor.
Fig. 2 is Fig. 1 " A " portion, i.e. the sectional drawing of existing drain tap device.
Fig. 3 is the part sectioned view of turbocompressor of the present invention.
Fig. 4 is Fig. 3 " B " portion, the sectional drawing of drain tap device promptly of the present invention.
Fig. 5 is the three-dimensional exploded view of drain tap device of the present invention.
Fig. 6 and Fig. 7 are the sectional drawings of drain tap device each several part working state of the present invention.
Fig. 8 and Fig. 9 are another embodiment's of exhaust port of the present invention schematic representation.
Figure 10 is another embodiment's of a drain tap device of the present invention sectional arrangement drawing.
1 ... shell 2 ... main frame
3 ... motor 4 ... live axle
5 ... rotary turbine 5a ... the lap of pressing chamber P
6 ... fixed turbine 6a ... the lap of pressing chamber P
6b ... suction port 6c ... exhaust port
7 ... high low pressure demarcation strip 8 ... the valve for preventing reverse-flow door assembly
9A ... valve 9B ... fixture
9C ... screw 10 ... valve portion
11 ... exhaust port 11a ... first passage
11b ... second channel 11c ... third channel
12 ... valve 13 is adjusted in exhaust ... valve actuator
13a ... four-way 14 ... buffering collapse coil spring
22 ... valve 32 is adjusted in exhaust ... valve is adjusted in exhaust
Embodiment
Below in conjunction with accompanying drawing and preferred embodiment, anti-its embodiment of overcompression device, structure, feature and the effect thereof of the turbocompressor that foundation the present invention is proposed, describe in detail as after.
See also Fig. 3, Fig. 4, Fig. 5, Fig. 6, shown in Figure 7, Fig. 3 is the part sectioned view of turbocompressor of the present invention, Fig. 4 is Fig. 3 " B " portion, it is the sectional drawing of drain tap device of the present invention, Fig. 5 is the three-dimensional exploded view of drain tap device of the present invention, and Fig. 6 and Fig. 7 are the sectional drawings of drain tap device each several part working state of the present invention.The anti-overcompression device of turbocompressor of the present invention, it mainly comprises: the shell 1 with gas suction pipe SP and gas outlet pipe DP; Be fixed on the main frame 2 and the auxiliary frame (not shown) of the both sides up and down of shell 1 inner peripheral surface; Be installed in main frame 2 and the auxiliary frame drive motor 3 between not shown; Be embedded in the center of drive motor 3, and pass the live axle 4 that main frame 2 is passed on the rotating force of drive motor 3; Combine with live axle 4, and be installed in the rotary turbine 5 of main frame 2 upper ends; Be combined in rotary turbine 5, and for forming the fixed turbine 6 that a plurality of pressing chambers are fixed on main frame 2 upper ends; Be combined in the back side of fixed turbine 6, and offset the discharge noise of the gas discharged, and be suction chamber S1 and the high low pressure demarcation strip 7 of discharging chamber S2 the internal separation of shell 1; Be combined in the back side of the lightweight plate portion of fixed turbine 6, and prevent to discharge the valve for preventing reverse-flow door assembly 8 of the adverse current phenomenon of gas; Be arranged on the fixed turbine 6, and when high-pressure ratio is moved, a part of pressurized gas in the pressing chamber P be discharged in advance the valve portion 10 of discharge chamber S2.
As Fig. 4 and shown in Figure 5, valve portion 10 includes as the bottom: enter into the exhaust port 11 of discharging chamber S2 and formation being set in order to make gas from the intermediate compression chambers P of the exhaust port 6c anteposition of fixed turbine 6; Be inserted into exhaust port 11 with axle direction, and in the high-pressure ratio operation, open above-mentioned exhaust port 11, and with a part of pressurized gas, valve 12 is adjusted in the exhaust of discharging in advance before discharging; Be embedded into the outlet of exhaust port 11, and the valve actuator 13 of the opening degree of valve 12 is adjusted in the control exhaust.
As Fig. 4 and shown in Figure 5, exhaust port 11 is a benchmark with the passage of pressurized gas, is formed on the exhaust port 6c anteposition of fixed turbine 6, and includes as the bottom and constitute: get through formation from middle pressing chamber P to discharging the chamber, have the first passage 11a of certain altitude; Begin to extend to the back side of fixed turbine 6 from the end of first passage 11a, and portion inserts the second channel 11b that valve 12 is adjusted in exhaust within it with same diameter always; Get through formation from the side of second channel 11b to discharging chamber S2, and in the high-pressure ratio operation, the third channel 11c that interconnects with first passage 11a.
Usually, the boundary face of first passage 11a and second channel 11b is designed to almost approach the right angle for the most desirable when the side projection, but as the case may be, also can be designed to internal conical surface shape as shown in Figure 9, and the exhaust that at this moment will meet the boundary with the boundary face of first passage 11a and second channel 11b is adjusted valve 32 and preferably also is designed to corresponding therewith outer conical surface shape.
In addition, a plurality of third channel 11c be tilted get through at a certain angle and be arranged on from the sidewall of second channel 11b until till the back side of fixed turbine 6, and each the third channel 11c of stable property that starts for valve is set to ideal with same inclination.Also have, when exhaust adjustment valve 12 is closed and opened, the inlet of third channel 11c is set in place the outside, field of adjusting valve 12 in its exhaust.
As Fig. 4 and shown in Figure 5, have certain volume for making exhaust adjust valve 12, it is arranged to ball-type.For the external diameter that makes ball is contacted with the internal diameter of second channel 11b, the phenomenon of touching in the time of can preventing to open and close, therefore the external diameter of ball is set to above-mentioned same size.
As shown in Figure 8, as the case may be, valve 22 is adjusted in above-mentioned exhaust also can be designed to piston-shaped excellent type.At this moment, adjust the lower end of valve 22 and carry out precision machining exhaust, to prevent the phenomenon that leaks outside of pressurized gas with the first passage 11a of lower end subtend and the boundary face of second channel 11b.
As Fig. 4 and shown in Figure 5, valve actuator 13 is designed to have the disc-shape of prescribed volume, part forms through hole in the central---and when normal operation, make the pressurized gas of discharge chamber flow into second channel 11b and the direction pressurization of valve 12 to first passage 11a adjusted in exhaust; On the contrary, when moving, can discharge as early as possible and remain in the cooled gas that the pressure back side of valve 12 is adjusted in exhaust, thereby make valve 12 open the four-way 13a of third channel 11c with high-pressure ratio.As shown in the figure, valve actuator 13 can embed, or as the case may be in order to ensure Security, also can assemble with screw.
In addition, adjusting the inside of valve 12 valve actuator 13 vis-a-vis with exhaust, can add as shown in figure 10, the buffering of the collision in the time of can alleviating exhaust and adjust valve 12 and open is with collapse coil spring 14.
In above-mentioned figure, represent the part identical with existing turbocompressor with same label symbol.
The lap that undeclared mark 5a is a rotary turbine among the above-mentioned figure, 6a are the lap of fixed turbine, and 6b is a suction port, and 0 is the anti-rotation accessory open loop damping ring (oldham) of rotary turbine.
Aforesaid anti-overcompression device according to turbocompressor of the present invention has following effect and effect.
Live axle 4 rotates with drive motor 3 because of additional power source, thereupon, rotary turbine 5 rotates to the position that is equivalent to eccentric distance, meanwhile, between lap 5a, the 6a of rotary turbine 5 and fixed turbine 6, form a plurality of pressing chamber P in couples, this pressing chamber P is again along with the continuous rotating motion of rotary turbine 5 is moved to the center, and carries out the process that reduces to absorb, compress and discharge cooled gas because of volume repeatedly.
At this moment, when operating pressure than and the pressure ratio of design is much the same or with low-pressure when normally moving, as shown in Figure 6, the pressure that is higher than pressing chamber P because of the pressure of discharging chamber S2, thereby make a part of pressurized gas of discharging chamber S2 flow into second channel 11b by the four-way 13a of valve actuator 13 and the third channel 11c of fixed turbine 6, and pressing above-mentioned exhaust to adjust valve 12, cutting off between first passage 11a and the second channel 11b.
On the contrary, when operating pressure than being higher than design pressure when promptly moving with high-pressure ratio, as shown in Figure 7, because of the pressure of intermediate compression chambers P is higher than the pressure of discharging chamber S2, thereby make exhaust adjust valve 12 because of above a part of pressurized gas that is discharged to first passage 11a is moved to.At this moment, because of exhaust is adjusted valve 12 along with second channel 11b up moves, third channel 11c also is opened, thereby first passage 11a and third channel 11c are interconnected by second channel 11b, make a part of pressurized gas of pressing chamber P before arriving exhaust port 6c, be discharged to discharge chamber S2 in advance.Thereby make the operating pressure ratio of pressing chamber P be lower than the design pressure ratio, and prevent the compression loss that causes because of excess compression.
As mentioned above, valve design globulate or clavate are adjusted in exhaust, and be embedded in the exhaust port, thereby make assembling process become simple and easy, and can improve the producibility of compressor, the problem of the reduction compressor reliability that the error when preventing because of the assembling between exhaust adjustment valve and the exhaust port in advance causes.
In addition, the depths that valve is inserted into exhaust port is dearly adjusted in exhaust, thereby reduced the volume of the exhaust port in normal when operation to a great extent, for example the volume of first passage has obviously reduced the volume of compressor, thereby improves the efficient of compressor.
The technological innovation of the anti-overcompression device of the turbocompressor of the present invention that above-mentioned structure like this constituted all has many saving graces for technician of the same trade now, and the progressive that possesses skills really.
The above, it only is preferred embodiment of the present invention, be not that the present invention is done any pro forma restriction, every foundation technical spirit of the present invention all still belongs in the scope of technical solution of the present invention above any simple modification, equivalent variations and modification that embodiment did.
Claims (8)
1, a kind of anti-overcompression device of turbocompressor, it comprises fixed turbine and is engaged in the rotary turbine that rotatablely moves on the said fixing turbine and form the pressing chamber that moves continuously, and comprise when the operating pressure ratio between suction pressure and the discharge pressure is higher than the design pressure ratio, for being rejected in advance, a part of pressurized gas before will discharging discharges the chamber, thereby prevent the overcompression phenomenon, with the fluid passage is benchmark, exhaust port the place ahead at fixed turbine or rotary turbine is provided with exhaust port, and it is characterized in that: it also comprises
Insert from the inside of exhaust port,, axially carry out smooth motion, and have the exhaust adjustment valve of the effect of opening or closing above-mentioned exhaust port along with the pressure difference between pressing chamber and the discharge chamber; And
Be combined in the valve actuator of above-mentioned exhaust port end for the sliding movement setting of control exhaust adjustment valve.
2, the anti-overcompression device of turbocompressor according to claim 1 is characterized in that wherein said exhaust port comprises: get through the first passage of formation from pressing chamber to discharging the chamber; Extend and form from the end of first passage, and portion embeds the second channel that valve is adjusted in above-mentioned exhaust within it; And get through formation, and when high-pressure ratio is moved, has the third channel that is communicated with first passage more than 1 at least from the side of second channel to discharging the chamber.
3, the anti-overcompression device of turbocompressor according to claim 2 is characterized in that the boundary face of wherein said first passage and second channel is scalariform.
4, the anti-overcompression device of turbocompressor according to claim 3 is characterized in that wherein said exhaust adjustment valve is provided with spherical in shape.
5, the anti-overcompression device of turbocompressor according to claim 3 is characterized in that the setting of wherein said exhaust adjustment valve is clavate.
6, the anti-overcompression device of turbocompressor according to claim 2, the boundary face setting that it is characterized in that wherein said first passage and second channel is the internal conical surface shape, and adjusts the valve setting with the exhaust on the boundary boundary that face connects of first passage and second channel and be corresponding therewith outer conical surface shape.
7, the anti-overcompression device of turbocompressor according to claim 2, the middle body hollow that it is characterized in that wherein said valve actuator forms when compressor normally moves, make the pressurized gas of discharging the chamber flow into second channel, and the direction pressurization of valve to first passage adjusted in exhaust; On the contrary, when moving, can discharge the four-way of the fluid at the pressure back side that remains in exhaust adjustment valve with high-pressure ratio.
8, the anti-overcompression device of turbocompressor according to claim 1, the inside that it is characterized in that the valve actuator that wherein said exhaust adjustment valve is relative, also be provided with and alleviate the collision that takes place when valve opening is adjusted in exhaust, play the buffer unit of buffer function.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB031377793A CN100378336C (en) | 2003-06-23 | 2003-06-23 | Overcompression prevention device for tubine compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB031377793A CN100378336C (en) | 2003-06-23 | 2003-06-23 | Overcompression prevention device for tubine compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1566708A true CN1566708A (en) | 2005-01-19 |
| CN100378336C CN100378336C (en) | 2008-04-02 |
Family
ID=34470540
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031377793A Expired - Fee Related CN100378336C (en) | 2003-06-23 | 2003-06-23 | Overcompression prevention device for tubine compressor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100378336C (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111120270A (en) * | 2019-12-26 | 2020-05-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Exhaust self-adjusting device, exhaust self-adjusting method and compressor |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5203857A (en) * | 1990-06-01 | 1993-04-20 | Bristol Compressors, Inc. | Gas compressor head and discharge valve construction |
| US5173042A (en) * | 1991-11-04 | 1992-12-22 | General Motors Corporation | Scroll compressor and discharge valve |
| JPH08319973A (en) * | 1995-05-26 | 1996-12-03 | Hitachi Ltd | Compressor and delivery valve device therefor |
| JPH0942175A (en) * | 1995-07-28 | 1997-02-10 | Mitsubishi Heavy Ind Ltd | Scroll compressor |
| JPH10331788A (en) * | 1997-05-30 | 1998-12-15 | Sanyo Electric Co Ltd | Oil removing device for scroll compressor |
| JP2001073972A (en) * | 1999-09-06 | 2001-03-21 | Toyota Autom Loom Works Ltd | Discharge structure of scroll compressor |
| US6257852B1 (en) * | 1999-12-06 | 2001-07-10 | Rechi Precision Co., Ltd. | Balancing structure of axial submission device for scroll compressor |
| JP2001323881A (en) * | 2000-05-16 | 2001-11-22 | Hitachi Ltd | Compressor |
-
2003
- 2003-06-23 CN CNB031377793A patent/CN100378336C/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111120270A (en) * | 2019-12-26 | 2020-05-08 | 珠海格力节能环保制冷技术研究中心有限公司 | Exhaust self-adjusting device, exhaust self-adjusting method and compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100378336C (en) | 2008-04-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1276180C (en) | Vaccum preventing device for vortex complessor | |
| CN1267646C (en) | Antivacuum device for vortex compressor | |
| CN1246590C (en) | Vacuumproof device for vortex type compressor | |
| CN1249350C (en) | Vacuum-protective device for vortex compressor | |
| CN1219981C (en) | Vacuum preventer for vortex compressor | |
| CN1865705A (en) | Scroll compressor | |
| CN1773120A (en) | Apparatus for varying capacity of scroll compressor | |
| CN1309959C (en) | Displacement changing device of vortex compressor | |
| CN1793653A (en) | Apparatus for varying capacity in scroll compressor | |
| CN1492151A (en) | Gas compressor | |
| CN1789726A (en) | Back pressure apparatus for orbiting vane compressors | |
| CN1950610A (en) | Rotary fluid machine | |
| CN100340768C (en) | Vortex compressor | |
| CN1815027A (en) | Step-type capacity varying apparatus of scroll compressor | |
| CN1566708A (en) | Overcompression prevention device for tubine compressor | |
| CN1320282C (en) | Vortex compressor having device for preventing noise | |
| CN1924358A (en) | Eddy liquid machinery | |
| CN1611787A (en) | Impact and noise reduction device for vortex compressor | |
| CN1690433A (en) | Screw compressor | |
| CN1955481A (en) | Variable capacity vortex compressor | |
| CN1239827C (en) | Vortex compressor manufacture method and apparatus | |
| CN100343517C (en) | Static vortex pan of vortex compressor | |
| CN1712728A (en) | Capacity-changer of rotary compressor | |
| CN100339599C (en) | Apparatus for decreasing vortex compressor noise | |
| CN1779268A (en) | Check valve device of reel-style compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080402 Termination date: 20110623 |