CN1083944C - Fluid machinery - Google Patents
Fluid machinery Download PDFInfo
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- CN1083944C CN1083944C CN98120757A CN98120757A CN1083944C CN 1083944 C CN1083944 C CN 1083944C CN 98120757 A CN98120757 A CN 98120757A CN 98120757 A CN98120757 A CN 98120757A CN 1083944 C CN1083944 C CN 1083944C
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- mechanical part
- axle
- engine according
- compression
- compression engine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
Abstract
A fluid machine capable of reducing the weight of a closed casing and ensuring smooth lubrication for a compression mechanism is disclosed. An intake gas is led into a closed casing(1)installing therein with a motor mechanism(7)and a compressor mechanism(9)rotated by a torque from the motor mechanism(7), and is compressed by the compressor mechanism(9). Thus compressed gas is discharged from the casing(1). The compressor mechanism(9)is arranged above the motor mechanism(7). A low pressure atmosphere is maintained in the closed casing(1)so that intake gas can be fed into the casing.
Description
The present invention relates to be fit to compress the helical blade type fluid compression engine of the gas refrigerant in the freeze cycle for example.
Constituting of traditional helical blade type fluid compression engine, eccentric configuration roller piston in cylinder body is wrapped in blade in the spiral groove that is formed on this roller piston outer circumferential face and forms pressing chamber in cylinder body.By the relative movement of cylinder body and roller piston, will transport successively toward the discharge side of cylinder body from the refrigerant limit of cylinder body suction side suction pressing chamber and compress, in case be about to its discharge after being full of pressurized gas in the closed shell.
The helical blade type fluid compression engine is owing to following reason, that is, and and the 1st, import compression mechanical part because directly will suck gas, be expelled in the closed shell after the compression, send outside the housing from the discharge tube of being located at housing again, so, be high-pressure gas medium in the closed shell.
The 2nd, because the relation of compression structure, press part extends vertically, so the distance of bearing.
The 3rd, the part of compression mechanical part faces under the liquid level of lubricant oil.
Therefore, the lubricant oil in being full of the closed shell of high-pressure gas medium has dissolved in a large amount of refrigerant, and oily temperature is high again, so viscosity easily descends, like this, for the helical blade type fluid compression engine of bearing distance, insufficient lubrication takes place the bearing of compression mechanical part easily.
In addition, if refrigerant is the high-pressure refrigerant that uses HFC series R410A for example, because compare with traditional R22, saturation pressure is up to about 1.5 times, so must fully guarantee the voltage endurance capability of high-pressure sealed housing.Therefore, must increase the wall thickness of closed shell, cause weight to increase, and also unfavorable aspect cost.
In addition, promptly stir lubricant oil, so can cause occurring the problem of bumpy running states such as oil supply instability, cogging and input increase if be positioned at the roller rotation of the compression mechanical part under the liquid level.
Therefore, the object of the present invention is to provide a kind of fluid compression engine that can prevent the bearing part generation insufficient lubrication of compressor.
In order to achieve the above object, a kind of fluid compression engine provided by the invention, configuration comprises the compression mechanical part of cylinder body, roller and blade and the mechanism portion that drives this compression mechanical part in closed shell, to suck gas imports in the described closed shell, and will directly be discharged to outside the described closed shell at the gas after the compression mechanical part compression, simultaneously, compression mechanical part is configured in the top of mechanism portion.
As preferable example, the compression direction of the pressing chamber of compression mechanical part is set at, and sucks gas from the below, compresses upward.
Perhaps, be designed to suck gas and suck pressing chamber from the cylinder body outer circumferential face.
Perhaps, be designed to suck gas and suck pressing chamber from the roller bottom.
If adopt such fluid compression engine, suck gas energy and lubricating oil separation, sent in the pressing chamber expeditiously.Because in closed shell, be full of the gas medium of the low pressure that sucks gas formation,, can have guaranteed sufficient viscosity so lubricant oil can not be under pressure and the strong influence of temperature.Therefore, the long bearing of adjusting the distance can carry out good lubricated.And the wall thickness of energy attenuate closed shell, weight reduction.And roller can not stir lubricant oil, can obtain the steady running state of compression mechanical part.
In addition, in the present invention, when the lubricant oil behind lubricated the end falls downwards, but fall into stator region after making the oily passage on the 1st bearing support of the axle of lubricant oil by being located at the free rotary ground supporting compression mechanical part of bearing of portion of lubricated overcompression mechanism, so that lubricant oil can outwards not thrown away because of the rotor of the mechanism portion of rotation.
Perhaps, form the 1st chamber volume that communicates with final pressing chamber on cylinder body, and the 2nd chamber volume that communicates with the 1st chamber volume is set above cylinder body, discharge gas and lubricating oil separation so that make, noise reduction also reduces resistance.
At this moment, the section of the 1st chamber volume is enlarged towards the 2nd chamber volume.
In addition, in order to stop the reverse flow of discharging gas, on the connection mouth that connects the 1st chamber volume and the 2nd chamber volume, be provided with and prevent that fluid is from the one-way valve of the 2nd chamber volume to the 1st chamber volume reverse flow.
Perhaps, the either party among the 2nd chamber volume side or roller end face side is provided with the annular seal device that high-pressure area and area of low pressure are sealed, and makes the center of annular seal device consistent with the axle center of axle.
At this moment, be preferably on the lower part wall of the 2nd chamber volume, but the bearing of formation free rotary ground supporting axle upper end portion.
Perhaps, by at the feeding gallery of the up/down perforation of being located at axle and be formed at bearing space between a upper end portion and the bearing, but the bearing surface of the 2nd bearing support of free rotary ground supporting axle upper end portion is lubricated, reliably to guarantee the lubricated of the topmost part position.
At this moment, preferably make the feeding gallery axle center biasing of axle relatively of being located at axle, rise smoothly so that lubricant oil is subjected to centrifugal action.
Perhaps, the feeding gallery of being located at axle is communicated, so that slide part is stablized oil supply respectively with the bearing bottom of the 1st bearing support and the bearing top of roller.
Perhaps, in order to prevent the influence of mechanism portion swing, axle is also used as the axle of mechanism portion, but and with the 3rd bearing support free rotary ground supporting penetrate mechanism portion spool shaft end.
Perhaps, in order to guarantee the centrifugal balance of compression mechanical part, on the axle of compression mechanical part, the 1st counterweight and the 2nd counterweight that is disposed in the roller is set respectively.
Perhaps, in order to prevent to suck the heating of gas and being involved in of lubricant oil, the compression direction of the pressing chamber of compression mechanical part is set at, sucks gas from the top and compress downwards.
Perhaps, in the discharge side of the roller that constitutes compression mechanical part, the seal arrangement of sealed high pressure portion and low voltage section is set, to guarantee to discharge the stable sealing state in territory, lateral areas.
Perhaps, form the chamber volume that communicates with final pressing chamber at the peripheral part of the cylinder body that constitutes compression mechanical part, with acquisition erasure effect.
Perhaps, the terminal assembly department of mechanism portion is installed in the zone of compression mechanical part and has on the closed shell of the area of space relative, so that can carry out distribution with beeline with cylinder body.
At this moment, the terminal assembly department preferably is configured in the notch part of the 1st bearing support of supporting compression mechanical part axle.
Perhaps, to apply the Euclidean ring that rotatablely moves to the roller of compression mechanical part and be arranged at the 1st bearing support, and be arranged at the lubricant oil that makes behind lubricated the end and fall between oily passage area and the roller downside in the stator region, so that prevent that as rotation the Euclidean ring of locking mechanism is in lubricating status all the time.
Perhaps, a kind of simple for structure, fluid compression engine that can stop mechanism portion swing disposes compression mechanical part that comprises cylinder body, roller and blade and the mechanism portion that drives this compression mechanical part in closed shell,
To suck gas imports in the described closed shell, and will be discharged to outside the closed shell at the gas after the compression mechanical part compression, simultaneously, compression mechanical part is configured in the top of mechanism portion, and clip mechanism portion, but run through the axle of compression mechanical part and mechanism portion with the bearing support free rotary ground supporting at two places.
Brief description:
Fig. 1 is the cut-away illustration of fluid compression engine of the present invention.
Fig. 2 is the sectional view along the A-A line among Fig. 1.
Fig. 3 is for being located at suction port the cut-away illustration identical with Fig. 1 of the 1st bearing support.
Fig. 4 makes suction port and suction pipe be located at the identical cross-sectional schematic with Fig. 1 of relative position.
But Fig. 5 for the 1st bearing support and the 3rd bearing support free rotary ground supporting axle, omitted the cross-sectional schematic identical of the 2nd bearing support with Fig. 1.
Fig. 6 is with Fig. 1 identical cross-sectional schematic of compression direction for compressing from the top down of compression mechanical part.
The drawing that below sees figures.1.and.2 specifies example of the present invention.
In Fig. 1,1 is depicted as the closed shell of the employed closed type fluid compression engine 3 of freeze cycle.Be provided with the suction pipe 5 of freeze cycle on the outer circumferential face of closed shell 1, dispose respectively in inside as the mechanism portion 7 of drive unit with as the compression mechanical part 9 of compression set, compression mechanical part 9 is configured in the top of mechanism portion 7.
The axle that axle 13 is also used as compression mechanical part 9 is the long shape of above-below direction, by following 3 supportings: but be fixed in housing 1 internal face and pass through the 1st bearing support 19 of the roughly intermediate portion of the 19a of bearing portion free rotary ground supporting axle 13; But the 2nd bearing support 21 by the 21a of bearing portion free rotary ground supporting axle 13 upper end portions; But the 3rd bearing support 23 by the 23a of bearing portion free rotary ground supporting axle 13 underparts.But, come two supports because put on axle 13 gas load by the 1st bearing support 19 and the 2nd bearing support 21 through eccentric axial portion 31, so consider, also can not dispose the 3rd bearing from the angle that stands gas load.
At compression mechanical part 9, by above-mentioned the 1st bearing support 19 and the 2nd bearing support 21 fixed bearings inside of the cylinder body 25 at two ends up and down, roller 27 cylindraceous is arranged along the axial arrangement of cylinder body 25.Bearing portion 29 intercalations of roller 27 are on the eccentric axial portion 31 of axle 13, and the periphery of roller 27 is by the Euclidean ring 33 of back with explanation, and its part contacts with the inner peripheral surface line of cylinder body 25, is applied in rotatablely moving of no rotation simultaneously.
In the inboard of roller 27, for the centrifugal force that makes axle 13 eccentric axial portion 31 averages out, clip eccentric axial portion 31, dispose a pair of counterweight 35 and the 2nd counterweight 37 up and down that are fixed in above-mentioned axle 13 respectively.The 2nd counterweight also can be disposed at the upper-end surface of rotor 15.At this moment, because the thickness of energy attenuate counterweight, so can reduce windage loss.Be provided with spiral helicine groove 39 on roller 27 outer circumferential faces, this spiral groove 39 is set at, and sucks the spacing maximum of distolateral (drawing downside), then along with trend discharge distolateral (drawing upside) spacing diminishes successively.
Setting-in spiral helicine blade 41 in spiral groove 39, and this blade 41 utilizes elastic force and gas pressure freely to stretch out or this groove of retraction.Therefore form each pressing chamber 43 and suck the volume maximum of distolateral pressing chamber 43.And be set at along with trend becomes the volume of discharging distolateral each pressing chamber 43 of top and diminish successively, the compression direction of pressing chamber 43 is, imports from the below suction port 45 of being located at cylinder body 25 and sucks gases, compresses towards the top again.
The final pressing chamber 43 that becomes the discharge side is guaranteed sealing by being located at contacted the 2nd bearing support 21 in roller 27 upper-end surfaces and by flexibly mounted annular seal 47 with interior all sides space of roller 27, is connected with the 1st chamber volume simultaneously.
Under this example, as the formation of Sealing 47, also can form annular slot at the 2nd bearing support 21, at the end of this annular slot configuration elastomer, between the upper-end surface of elastomer and roller 27, insert seal ring to guarantee sealing.
The 1st chamber volume 49 is connected by the 2nd bigger chamber volume 53 of connecting port 51 and volume, and the 2nd chamber volume 53 is connected with the discharge tube 55 that extends outside closed shell 1.
Make the section of the 1st chamber volume 49 have tapering ground to enlarge, can reduce the fluid passage loss towards connecting port 51.
Be provided with one-way valve 57 in the outlet port of connecting port 51, when stopping with the prevention compression operation, the discharge gases in the 2nd chamber volume 53 return in the 1st chamber volume 49.
The 2nd chamber volume 53 has silencing function and the oil of realizing noise reduction and separates function, and the lower part wall of the 2nd chamber volume 53 is formed by the 2nd bearing support 21, and top wall is formed by the discharge cover 59 that is fixed in the 2nd bearing support 21.At this moment,, be provided with to lead to outside lubricant oil guiding channel 61 or capillary tube, can make the smooth and easy bottom of returning closed shell 1 of lubricant oil after the separation, guarantee the lubricant oil in the housing 1 by shown in the imaginary line in the 2nd chamber volume 53.
The exhaust end 63a that is located at the oily passage 63 of the 1st bearing support 19 is positioned at the top of stator 11 regions of mechanism portion 7, and lubricant oil can directly not fallen on the rotor rotated 15.
On the other hand, to the terminal assembly department 17 of stator 11 supplying electric currents as shown in Figure 2, be installed on the outer circumferential face of closed shell 1 and be configured in the notch part 65 of above-mentioned the 1st bearing support 19.The whole height that therefore, can suppress closed shell 1.
At this moment, the 21a of bearing portion of the 2nd bearing support 21 is that the bearing space 71 by the axle upper end portion is connected, but also can be connected by passage.Adopt this structure, because the lubricant oil of closed shell 1 bottom can be picked up the bearing space 71 that the bearing 21a of portion is directly supplied with in the back by pump 69, so can guarantee reliability.
In addition, near the eccentric axial portion 31 of roller 27, be provided with the intercommunicating pore 27a of up/down perforation.Therefore, the oil behind the 21a of lubricating bearings portion can fall downwards by intercommunicating pore 27a always.Again, as the position of giving oilhole, portion formed thereon on eccentric axial portion 31, lubricant oil is flowed from the top down, on the 19a of bearing portion of the 1st bearing support 19, then be formed at the bottom, if lubricant oil is flowed from bottom to top, then oil lubrication the slide part of the lower end surface of roller 27 and Euclidean ring 33 be after the fitting projection 33b, by oily passage 63, can not returned the bottom of closed shell 1 by rotor with scrolling up.Therefore, high reliability is guaranteed in the circulation that the lubricant oil in the closed shell 1 can reliably carry out oil supply, lubricate, returns.
Fig. 3 shows the example of suction port 45 being located at the 1st bearing support 19.
That is, because suction port 45 is disposed at the bottom of compression mechanical part 9, can not be heated so suck gas, compression efficiency improves.
And for example shown in Figure 4, be provided with in the example of suction pipe 5 in the position relative with suction port 45, also can be provided with and will suck the guide plate 73 of gas below guiding at suction pipe 5, with it as making refrigerant run into the devices that guide plate 73 backs and suction gas are separated.
In addition, shown in imaginary line, breach wall 75 is set on the cylinder body below the suction port 45 25, and the not shown suction pipe 5 relative with this breach wall 75 is set, just can omit guide plate 73.
If this breach wall 75 is enlarged with above-mentioned guide plate 75 the same inclinations and to downside, then refrigerant is easy to fall downwards, can guarantee the separating effect of gas and liquid.
But Fig. 5 shows the example with 2 free rotary ground supporting axles 13.
That is, but the axle that runs through compression mechanical part 9 and mechanism portion 7 has omitted bearing on the 2nd bearing support 21 of upper end portion side 13 by the 1st bearing support 19 and the 3rd bearing support 23 free rotary ground supportings.
On axle 13, sandwich eccentric axial portion 31 is being fixed the 1st counterweight 77 and the 2nd counterweight 79, and the 1st counterweight 77 of axle 13 upper end portions utilizes wider space can select the little arbitrary shape of windage loss.
About other constituting component, since same as shown in Figure 1, so put on identical symbol and detailed.
Therefore, if adopt this example, then except the effect of device shown in Figure 1, also come supporting axle 13 with the 1st bearing support 19 and the 3rd bearing support 23, because the gas load that takes place at pressing chamber is by eccentric axial portion 31 supportings of axle 13, so, when as this helical impeller compressor owing to there is press part than length to make spools 13 when longer, because of the 1st bearing support 19 is separated with the distance of the 3rd bearing support 23, so can alleviate the 1st and the 3rd bearing support 19,23 loads.
This is because if the load that facility is added on eccentric axial portion 31 is F, the load that puts on the 1st and the 3rd bearing support 19,23 is respectively F
1, F
2, the distance of eccentric axial portion 31 to the 1st bearing supports 19 and be respectively L to the distance of the 3rd bearing support 23
1, L
2, then:
F·L
1＝F
2·L
2……(1) F+F
2＝F
1……(2)
Because the left side in the formula (1) is certain, so L
2F during increase
2Diminish, find out F from formula (2)
2Little then F
1Also little.Like this, load can be supported by the 1st and the 3rd bearing support 19,23, so can omit the 2nd bearing support 21, does not need very high mounting technology just can assemble.
Shown in Fig. 6 is that compression direction with compression mechanical part 9 is set at and sucks gas, the example that compresses from the top downwards.
That is,, by the 1st bearing support 81 and the 2nd bearing support 83 fixed bearings cylinder body 85 inside at two ends up and down, cylindric roller 87 is arranged along the axial arrangement of cylinder body 85 at compression mechanical part 9.Bearing portion 89 intercalations of roller 87 are in the eccentric axial portion 31 of axle 13, and by Euclidean ring 33, roller 87 peripheries are local on one side to be contacted as line with the inner peripheral surface of cylinder body 85, does rotatablely moving of no rotation simultaneously on one side.
In roller 87 inboards, for the eccentric axial portion 31 with axle 13 averages out, clip eccentric axial portion 31 on centrifugal force, on above-mentioned axle 13, fixing the 1st counterweight 91 and the 2nd counterweight 92 a pair of counterweight so up and down respectively.Roller 87 outer circumferential faces are provided with spiral helicine groove 93, and this spiral groove 93 is set at, and suck the spacing maximum of distolateral (drawing upside), and along with trend is discharged distolateral (drawing downside), spacing diminishes successively.
In spiral groove 93, intercalation has elastic force utilized and gas pressure to stretch out and the spiral blade 95 of retraction notch.Therefore form each pressing chamber 97, and suck the volume maximum of distolateral pressing chamber 97, and along with the trend discharge is distolateral, the volume of each pressing chamber 97 diminishes successively.The compression direction of pressing chamber 97 is, sucks gas and imports from the suction port 99 of the top of being located at cylinder body 85, and compress towards the below.
Become the nethermost last pressing chamber 97 of discharging side and guarantee sealing, communicate with the 1st chamber volume 103 simultaneously by the annular seal member of being located between roller 87 and the cylinder body 85 101.
The 1st chamber volume 103 communicates with capacious the 2nd chamber volume 105, and the 2nd chamber volume 105 communicates with discharge tube 107 outside extending to closed shell.
The 2nd chamber volume 105 has silencing function and the oil of realizing noise reduction and separates function.
At this moment, by leading to outside grease channel 109 or tubule as shown in phantom in FIG., make lubricant oil after the separation successfully return the bottom of closed shell 1 the setting of the 2nd chamber volume 105.
Other constituting component is same as shown in Figure 1, so put on same-sign and detailed.
Therefore, if adopt example shown in Figure 6, the suction gas of sending into from suction port is imported into pressing chamber 97 from the suction port 99 of top, is pressed downward and contracts.At this moment, because suction port 99 separates with suction pipe 5, so, can directly do not sucked suction port 99 from the refrigerant that returns of suction pipe 5, can prevent the excess load running.Again because suction port 99 is configured in the top of compression mechanical part 9, so suction gas can not be heated, and can improve volumetric efficiency.
In addition, when being helical impeller compressor, because gas load occurrence positions vertically is in the narrow and small discharge side of spacing from the blade 41 of the middle body of roller 87, so can make the gas load occurrence positions near drive electric motor structure portion 7, bearing load can alleviate the load of axle 13 bending force etc., so also can alleviate, can improve reliability, reduce loss.
On the other hand, pass through the 1st chamber volume 103 and the 2nd chamber volume 105 through the discharge gas of overcompression, be discharged to the outside through discharge tube 107 again at pressing chamber 97.Discharge gas by the 1st and the 2nd chamber volume 103,105 o'clock by noise reduction.
In addition, each 81a of bearing portion, 83a of the 1st, the 2nd bearing support 81,83 are lubricated by oily passage 67, can obtain long steady running state.
As mentioned above, if adopt the present invention, can obtain following effect.
(1) can not be subjected to the high temperature of lubricating oil, the strong effect of high pressure, the sliding part of compression mechanical part can obtain
Get lubricating status well.
(2) can make closed shell thin-walled property, weight reduction.
(3) can not stirred lubricating oil by roller, compression mechanical part can obtain stable operating condition.
(4) can be separated sucking gas and refrigerant, not suck refrigerant, prevent the overload running, and
Prevent from sucking the heating of gas, guarantee high efficiency compressive state.
Claims (23)
1. a fluid compression engine disposes compression mechanical part that comprises cylinder body, roller and blade and the mechanism portion that drives this compression mechanical part in its closed shell, it is characterized in that,
To suck gas and import in the described closed shell, and will directly be discharged to outside the described closed shell, simultaneously, compression mechanical part will be configured in the top of mechanism portion at the gas after the compression mechanical part compression.
2. fluid compression engine according to claim 1 is characterized in that, the compression direction of the pressing chamber of described compression mechanical part is that suction gas compresses upward from the below.
3. fluid compression engine according to claim 2 is characterized in that, will suck gas from described cylinder body outer circumferential face and suck pressing chamber.
4. fluid compression engine according to claim 2 is characterized in that, will suck gas from described roller bottom and suck pressing chamber.
5. fluid compression engine according to claim 1 is characterized in that, but falls in the stator region after making oily passage on the 1st bearing support of the axle of lubricant oil by being located at the free rotary ground supporting compression mechanical part of bearing of portion of lubricated overcompression mechanism.
6. fluid compression engine according to claim 1 is characterized in that, is formed with the 1st chamber volume that communicates with final pressing chamber on cylinder body, and is provided with the 2nd chamber volume that communicates with the 1st chamber volume above cylinder body.
7. fluid compression engine according to claim 6 is characterized in that, the section of the 1st chamber volume is enlarged towards the 2nd chamber volume.
8. fluid compression engine according to claim 6 is characterized in that, is provided with on the connection mouth that connects the 1st chamber volume and the 2nd chamber volume and prevents that fluid is from the one-way valve of the 2nd chamber volume to the 1st chamber volume reverse flow.
9. fluid compression engine according to claim 6 is characterized in that, the either party among the 2nd chamber volume side or roller end face side is provided with the annular seal device that high-pressure area and area of low pressure are sealed.
10. fluid compression engine according to claim 9 is characterized in that, the center of described annular seal device is consistent with the axle center of axle.
11. fluid compression engine according to claim 6 is characterized in that, on the lower part wall of the 2nd chamber volume, but is formed with the bearing of free rotary ground supporting axle upper end portion.
12. fluid compression engine according to claim 11, it is characterized in that, by at the feeding gallery of the up/down perforation of being located at axle and be formed at bearing space between a upper end portion and the bearing, but the bearing surface of the 2nd bearing support of free rotary ground supporting axle upper end portion is lubricated.
13. fluid compression engine according to claim 12 is characterized in that, is located at the described feeding gallery axle center biasing of axle relatively of axle.
14. fluid compression engine according to claim 13 is characterized in that, the described feeding gallery of being located at axle is connected respectively with the bearing bottom of the 1st bearing support and the bearing top of roller.
15., it is characterized in that described axle is also used as the axle of mechanism portion according to claim 12,13,14 described fluid compression engines, but and with the 3rd bearing support free rotary ground supporting penetrate mechanism portion spool shaft end.
16. fluid compression engine according to claim 1 is characterized in that, on the axle of described compression mechanical part, is respectively equipped with the 1st and the 2nd counterweight that is disposed at the roller inboard.
17. fluid compression engine according to claim 1 is characterized in that, the compression direction of the pressing chamber of described compression mechanical part is to suck gas from the top and also compress downwards.
18. fluid compression engine according to claim 17 is characterized in that, in the discharge side of the roller that constitutes described compression mechanical part, is provided with the seal arrangement of sealed high pressure portion and low voltage section.
19. fluid compression engine according to claim 17 is characterized in that, is formed with the chamber volume that communicates with final pressing chamber at the peripheral part of the cylinder body that constitutes described compression mechanical part.
20. fluid compression engine according to claim 1 is characterized in that, the terminal assembly department of described mechanism portion is installed in the zone of compression mechanical part and has on the closed shell of the area of space relative with cylinder body.
21. fluid compression engine according to claim 20 is characterized in that, described terminal assembly department is configured in the notch part of the 1st bearing support of axle of supporting compression mechanical part.
22. fluid compression engine according to claim 1, it is characterized in that, the anti-locking mechanism of the rotation that rotatablely moves that the roller of compression mechanical part is applied no rotation is arranged at the 1st bearing support, and is arranged at the lubricant oil that makes behind lubricated the end and falls between the oily passage area and roller downside in the stator region.
23. a fluid compression engine disposes compression mechanical part that comprises cylinder body, roller and blade and the mechanism portion that drives this compression mechanical part in its closed shell, it is characterized in that,
The suction gas of described compression mechanical part is imported in the described closed shell, simultaneously, compression mechanical part is configured in the top of mechanism portion, and clips described mechanism portion, but runs through the axle of compression mechanical part and mechanism portion with the bearing support free rotary ground supporting at two places.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP271635/97 | 1997-10-03 | ||
| JP9271635A JPH11107952A (en) | 1997-10-03 | 1997-10-03 | Fluid machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1213745A CN1213745A (en) | 1999-04-14 |
| CN1083944C true CN1083944C (en) | 2002-05-01 |
Family
ID=17502820
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN98120757A Expired - Fee Related CN1083944C (en) | 1997-10-03 | 1998-09-25 | Fluid machinery |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPH11107952A (en) |
| KR (1) | KR100297177B1 (en) |
| CN (1) | CN1083944C (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100640229B1 (en) * | 2000-12-07 | 2006-10-31 | 주식회사 엘지이아이 | A hermetic compressor |
| JP5911637B2 (en) * | 2013-03-05 | 2016-04-27 | 三菱電機株式会社 | Compressor |
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1997
- 1997-10-03 JP JP9271635A patent/JPH11107952A/en active Pending
-
1998
- 1998-09-25 CN CN98120757A patent/CN1083944C/en not_active Expired - Fee Related
- 1998-09-29 KR KR1019980040425A patent/KR100297177B1/en not_active IP Right Cessation
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4871304A (en) * | 1987-07-31 | 1989-10-03 | Kabushiki Kaisha Toshiba | Axial flow fluid compresser |
| US5174737A (en) * | 1990-06-28 | 1992-12-29 | Kabushiki Kaisha Toshiba | Fluid compressor with spiral blade |
| US5332377A (en) * | 1991-05-09 | 1994-07-26 | Kabushiki Kaisha Toshiba | Compressor with oversized blade |
| CN2130213Y (en) * | 1992-06-19 | 1993-04-21 | 西安交通大学 | Horizontal fully-closed vortex compressor |
| CN1116278A (en) * | 1994-02-16 | 1996-02-07 | 运载器有限公司 | Rotary compressor with liquid injection |
| US5542832A (en) * | 1994-03-31 | 1996-08-06 | Kabushiki Kaisha Toshiba | Rotary fluid compressor having an oldham mechanism |
| CN1116690A (en) * | 1994-06-02 | 1996-02-14 | Lg电子株式会社 | Rotary compressor |
| CN1140806A (en) * | 1995-05-04 | 1997-01-22 | 运载器有限公司 | Twin cylinder rotary compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH11107952A (en) | 1999-04-20 |
| KR19990036695A (en) | 1999-05-25 |
| CN1213745A (en) | 1999-04-14 |
| KR100297177B1 (en) | 2002-02-19 |
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| C14 | Grant of patent or utility model | ||
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