CN1692228A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
- Publication number
- CN1692228A CN1692228A CNA2003801004211A CN200380100421A CN1692228A CN 1692228 A CN1692228 A CN 1692228A CN A2003801004211 A CNA2003801004211 A CN A2003801004211A CN 200380100421 A CN200380100421 A CN 200380100421A CN 1692228 A CN1692228 A CN 1692228A
- Authority
- CN
- China
- Prior art keywords
- blade
- spring
- rotary compressor
- helical spring
- roller
- 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.)
- Pending
Links
Images
Classifications
-
- 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
- F04C18/356—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 outer member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0854—Vane tracking; control therefor by fluid means
- F01C21/0872—Vane tracking; control therefor by fluid means the fluid being other than the working fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/08—Rotary pistons
- F01C21/0809—Construction of vanes or vane holders
- F01C21/0818—Vane tracking; control therefor
- F01C21/0827—Vane tracking; control therefor by mechanical means
- F01C21/0845—Vane tracking; control therefor by mechanical means comprising elastic means, e.g. springs
-
- 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
- F04C18/356—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 outer member
- F04C18/3562—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
- F04C18/3564—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 outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
-
- 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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- 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
-
- 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
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/261—Carbon dioxide (CO2)
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
A rotary compressor that is downsized and is controlled for leakage of operating fluid. These are achieved by providing the compressor with a coil spring that presses a vane to a roller and securing sufficient contact area between the vane and a vane groove by a simple and inexpensive structure. A rotary compressor has a tightly closed container (1), a cylinder (4) provided inside the tightly closed container (1) and having a vane groove (4a), a shaft with an eccentric portion (5a), a roller (6) rotatably fitted on the eccentric portion (5a) of the shaft and eccentrically rotating inside the cylinder (4), a vane (7) provided in the vane groove (4a) of the cylinder (4) and reciprocally moving in the vane groove (4a) with the forefront of the vane being in contact with the roller (6), and a coil spring (20) pressing the vane (7) on the roller (6). The vane (7) is provided with a spring hole (7d) on the side opposite the side of the vane (7) that comes in contact with the roller (6). At least part of the coil spring (20) is received in the spring hole (7d).
Description
Technical field
The present invention relates to employed rotary compressors such as deep freezer, air conditioner.
Background technique
Fig. 4 is the longitudinal sectional view of the past rotary compressor, Fig. 5 is the transverse sectional view of the compression mechanical part of the past rotary compressor, shown in Figure 6 is the transverse sectional view of the compression mechanical part size of the past rotary compressor, and Fig. 7 and Fig. 8 are the stereograms of the blade of the past rotary compressor.
Rotary compressor is by seal container 1, is arranged at its inner compression mechanical part 2 and motor 3 is constituted.Compression mechanical part 2 is by the cylinder 4 that is provided with cylindrical part; With central axis L 1 is that the center can rotating bent axle 5; The roller 6 that the eccentric part 5a that is engaged in bent axle 5 goes up, follows the revolution of bent axle 5 to carry out eccentric rotation motion in the cylinder interior of cylinder 4; With the eccentric rotation motion of roller 6, the blade 7 that moves back and forth in the blade groove 4a inside of cylinder 4; Be arranged on the back side 7a of blade 7, the front end 7b of blade 7 be pressed on the spring mechanism 8 of helical spring on the roller 6 etc.; The both ends of the surface of gripper cylinder 4, can turn round the 1st radial bearing 9 of motor 3 sides that freely support bent axle 5; The 2nd radial bearing 10 of the opposition side of motor 3 constitutes.By formed supporting portion 4b around the cylinder 4 compression mechanical part 2 is fixed in the seal container 1.Motor 3 is made of the stator cylindraceous 11 of the inside that is welded on seal container 1, the shrink fit columned rotor 12 on bent axle 5.
Working fluid is fed in the pressing chamber that is made of cylinder 4, roller 6, blade the 7, the 1st radial bearing 9 and the 2nd radial bearing 10 from the inlet hole 4c of suction pipe 13 by cylinder 4.Make the roller 6 on the eccentric part 5a that is engaged in bent axle 5 that eccentric rotation motion takes place in the rotation motion that motor 3 is produced, change and make working fluid by compression thereupon the volume that makes pressing chamber 14.In case open the outlet valve (not illustrating) of exhaust port 15, working fluid by compression through the inside of seal container 1 by outlet pipe 16 by the outside of row to seal container 1.(consult " refrigerating and air conditioning brief guide, new edition the 5th edition, an II convolver piece of writing ", Japanese freezing association, put down into 5 years, the 30th～37 page)
Rotary compressor is when running well, and the power that is produced because of the difference force between the interior pressure of the pressing chamber 14 of the exhaust pressure that results from blade 7 back side 7a and the front end 7b that results from blade 7 and spring mechanism 8 is pressed on the front end 7b of blade 7 on the roller 6.But, just during setting in motion, be added in the exhaust pressure on the back side 7a of blade 7 and be added between the pressure in the pressing chamber 14 of front end 7b of blade 7 and have pressure reduction hardly, therefore, rely on power that spring mechanism 8 produced that the front end 7b of blade 7 is pressed on the roller 6.
In rotary compressor in the past, the spring mechanism 8 of helical spring etc., the one side end contacts with the back side 7a of blade 7, and the end of opposite side contacts with cylinder inner wall 1 a of seal container 1.When blade 7 when blade groove 4a moves back and forth, the back side 7a of blade is that the eccentric rotation motion because of roller 6, the front end 7b of blade 7 are press-fit into the state of the cylinder inner wall 4d of cylinder 4 near the state of the cylinder inner wall 1a of seal container 1.At this moment, the space more than the crush pad that must often guarantee spring mechanism 8 between the cylinder inner wall 1a of the back side of blade 7 7a and seal container 1.
Promptly, the internal diameter that the internal diameter that the crush pad of spring mechanism 8 is set at the cylinder inner wall 1a of 1cvm, seal container 1 is set at the cylinder inner wall 4d of dmi, cylinder 4 is set at dci, the length setting from the front end 7b of blade 7 to back side 7a is 1vn, and the inequality of formula 1 must be set up.
(several 1)
(d
Mi-d
Ci)/2＞1
Vn+ 1
Cvm Formula 1
When seal container 1 path of rotary compressor, the left side of formula 1 diminishes, and the crush pad 1cvm of the spring mechanism 8 on the right depends on the specification of spring mechanism 8.
Therefore, the length 1vn of blade 7 shortens, and the seal length between the auxiliary section of blade 7 and blade groove 4a shortens, and sealability reduces, owing to the pressure reduction between the pressure of the exhaust pressure of the back side 7a side that is directed to blade 7 and pressing chamber 14 produces the leakage of working fluid, so reduced compression efficiency.
And, eccentric rotation motion because of roller 6, under blade 7 state outstanding from the cylinder inner wall 4d of cylinder 4, pressure difference between the pressure of compression process and the pressure of suction process acts on the side 7c of the blade 7 in the pressing chamber 14, blade 7 is toppled over to blade groove 4a, because the length 1vn of blade 7 shortens, the length of thread engagement deficiency between blade 7 and the blade groove 4a is so dump angle increases.Therefore, because the interface pressure between blade 7 and the blade groove 4a rises, the loss that produces because of friction increases, so the efficient of compressor reduces.
And, rotary compressor in the past, as shown in Figure 8, employing be the back side 7a depression that makes blade 7, guarantee to hold the structure in the space of spring mechanism 8 with this.But, such structure, the length of the actual blade 7 relevant with the sealing of auxiliary section between blade 7 and the blade groove 4a shortens, and is the same with blade shown in Figure 7, can not prevent the decline of compression efficiency.
Summary of the invention
The objective of the invention is to eliminate the problem points of described the past, a part of having held the spring mechanism 8 of helical spring etc. by inside at blade 7, thereby guarantee area of contact between blade 7 and the blade groove 4a with simple, inexpensive structure, when suppressing the leakage of working fluid, can provide the rotary compressor of miniaturization.
In order to solve described problem, the present invention's the 1st technological scheme is a kind of rotary compressor, has: seal container; Be arranged in described seal container inside, be provided with the cylinder of blade groove; Be provided with the bent axle of eccentric part; Can be engaged in the roller that carries out eccentric rotation motion on the described eccentric part of described bent axle, in described cylinder interior freely to rotate; The blade that moves back and forth at described blade inside groove when being arranged in the described blade groove of described cylinder the preceding end in contact with described roller; Described blade is pressed on spring mechanism on the described roller, described blade, opposition side in the side that contacts with described roller of described blade is provided with spring eye, described spring eye is opened in the cross section perpendicular to the reciprocating described blade of described blade, is a part that accommodates described spring mechanism at least.
The present invention's the 2nd technological scheme is the described rotary compressor of the present invention's the 1st technological scheme, and described spring mechanism has a plurality of, and described blade has described a plurality of spring eye, accommodates the part of described spring mechanism in described each spring eye at least respectively.
The present invention's the 3rd technological scheme is the described rotary compressor of the present invention's the 1st technological scheme, and described spring mechanism is a helical spring.
The present invention's the 4th technological scheme is the described rotary compressor of the present invention's the 3rd technological scheme, a described helical spring end is housed inside in the described spring eye of described blade, is provided with the helical spring guide mechanism with the contacted base of the described helical spring the other end.
The present invention's the 5th technological scheme is the described rotary compressor of the present invention's the 4th technological scheme, and described helical spring guide mechanism is arranged on the inner side surface of described seal container.
The present invention's the 6th technological scheme is the described rotary compressor of the present invention's the 3rd technological scheme, the width of described blade is below the above 3.5mm of 3.0mm, the stroke of described blade is below the above 5.0mm of 3.0mm, described helical spring diameter is that 2.0mm is above less than 3.0mm, and described helical spring free length is below 5 times of diameter.
The present invention's the 7th technological scheme is the described rotary compressor of the present invention's the 1st technological scheme, and working fluid is a carbon dioxide.
According to the present invention, can be provided at simple, inexpensive structure and guarantee the area of contact between blade and the blade groove, the rotary compressor of energy miniaturization when suppressing the working fluid leakage.
The simple declaration of accompanying drawing
Fig. 1 relates to the stereogram of blade of the rotary compressor of the invention process form 1.
Fig. 2 relates near the transverse sectional view the blade groove of compression mechanical part of rotary compressor of the invention process form 1.
Fig. 3 relates near the transverse sectional view the blade groove of compression mechanical part of rotary compressor of the invention process form 2.
Fig. 4 is the longitudinal sectional view of rotary compressor in the past.
Fig. 5 is the transverse sectional view of the compression mechanical part of the past rotary compressor.
Fig. 6 is the transverse sectional view of the compression mechanical part size of the past rotary compressor.
Fig. 7 is the stereogram of the blade of the past rotary compressor.
Fig. 8 is the stereogram of the blade of the past rotary compressor.
Embodiment
Below describe with regard to several examples of the present invention with Fig. 1, Fig. 2 and Fig. 3.The following description is to state about instantiation of the present invention, is not the content that claims are put down in writing is limited.
The rotary compressor of several examples of the present invention is the structures about the rotary compressor except that cylinder 4, blade 7 and spring mechanism 8, what Fig. 4 was extremely shown in Figure 8 is and the identical structure of rotary compressor that identical constitutional detail has used identical numbering in the past.In addition, the structure identical and the explanation of effect have been omitted in the past with example.
[example 1]
Fig. 1 is the stereogram of the blade of the rotary compressor in the invention process form 1.Fig. 2 is near the transverse sectional view of blade groove of the compression mechanical part of the rotary compressor in the invention process form 1.The front end 7b of shown in Figure 2 is blade 7 is press-fit into the state of the cylinder inner wall 4d of cylinder 4.
This example, as shown in Figure 1, be provided with outside dimension less than the width of the back side 7a of blade 7 and the helical spring 20 of height as spring mechanism 8, the back side of blade 7 7a be provided with diameter greater than the external diameter of helical spring 20 less than the width of blade 7 and height, at the vibration-direction of blade 7,2 spring eye 7d of degree of depth 1vna, 2 spring eye 7d hold an end of helical spring 20 respectively, and the end of the anti-blade-side of helical spring 20 is contacted with cylinder inner wall 1 a of seal container 1.In addition, eccentric rotation motion with roller 6, present at the front end 7b that makes blade 7 under the state of the cylinder inner wall 4d face that is press-fit into cylinder 4, the length 1vn of blade 7 is the length of the inferior limit gap 1cr that produced between the cylinder inner wall 1a of the back side 7a of blade 7 and seal container 1.
Even if helical spring 20 crush pad under compressive state is not allowed below 1cvm yet, even blade 7 during from the most outstanding state of the cylinder inner wall 4d of cylinder 4 since helical spring 20 blade 7 is pressed on the roller 6, so helical spring 20 must (not illustrate) below free length 1cvf.Therefore, will follow the reciprocating stroke of blade 7 of the eccentric rotation motion of roller 6 to be set at lst, spring eye 7d be made of the degree of depth 1vna in the inequality of formula 2.
(several 2)
1
Cvm-1
Cr＜1
Vna＜1
Cvf-1
St-1
Cr Formula 2
The formed effect of described structure then is described.
Rotary compressor in this example, owing to held a part of helical spring 20 among the spring eye 7d of blade 7, eccentric rotation motion because of roller 6, make the front end 7b of blade 7 present the state of the cylinder inner wall 4d face that is press-fit into cylinder 4, between the cylinder inner wall 1a of the back side of blade 7 7a and seal container 1, can set the gap 1cr littler than the crush pad 1cvm of helical spring 20.Therefore, represent with formula 1, formula 3.
(several 3)
(d
Mi-d
Ci)/2＞1
Vn+ 1
Cr Formula 3
But as illustrated in the background technique, dmi is the internal diameter of the cylinder inner wall 1a of seal container 1, and dci is the internal diameter of the cylinder inner wall 4d of cylinder 4, and 1vn is the length of the front end 7b of blade 7 to back side 7a.
Promptly, rotary compressor in the past, when seal container 1 path, just shorten the length 1vn of blade 7, reduce the sealing in the auxiliary section between blade 7 and the blade groove 4a, and the rotary compressor in this example, even if the just crush pad 1cvm of helical spring 20 of the radius cripetura of seal container 1 and the difference part of gap 1cr, the length 1vn of blade 7 is preceding identical with pathization, add since the external diameter of spring eye 7d less than the width and the height of blade 7, side at blade 7 does not produce damaged, do not damage the length of auxiliary section between blade 7 and the blade groove 4a, so can keep the sealing of auxiliary section between blade 7 and the blade groove 4a.
That is, owing to can hold a part of helical spring 20 in the spring eye 7d of blade 7, even if make the rotary compressor pathization, the length of blade 7 is compared and can be increased with rotary compressor in the past.Thereby, compare with rotary compressor in the past, can keep the sealing of auxiliary section between blade 7 and the blade groove 4a more reliably.
And, rotary compressor in this example, even if be more than the difference of the crush pad 1cvm of helical spring 20 and gap 1cr when making the radius path of seal container 1, compare with the seal container 1 of the rotary compressor of in the past pathization, because the length 1vn of blade 7 increases, self-evident, can relax the reduction of the sealing of auxiliary section between blade 7 and the blade groove 4a.
And, compare with rotary compressor in the past, because length of thread engagement is elongated between blade 7 and the blade groove 4a, blade 7 diminishes with respect to the dump angle of blade groove 4a.Therefore, the surface of contact that has reduced between blade 7 and the blade groove 4a is pressed, easy tempered oil film, the reliability of raising slip surface.And, press because of the surface of contact that reduces between blade 7 and the blade groove 4a, reduced the caused loss of friction, also improve mechanical efficiency.
And, being provided with 2 spring eye 7d at the back side of blade 7 7a, 2 spring eye 7d accommodate the part of helical spring 20 respectively at least, owing to 2 springs can be pressed on blade 7 on the roller 6, so can reduce the spring constant of design helical spring 20.Therefore, the diameter of helical spring 20 can pathization, and the thickness of blade 7 can be not excessive, and obtain described effect.Especially, in the distributed locations of the back side of blade 7 7a, the spring force of helical spring 20 can play a role, therefore, the front end 7b of blade 7 can be pressed on equably on the roller 6, one-sided being pressed on the roller 6 of front end 7b of blade 7 can not taken place, can improve the reliability of the front end 7b of blade 7.In this example, just use 2 spring eye 7d and helical spring 20 to be illustrated respectively, but be not limited thereto, also can use spring eye 7d and helical spring 20 more than 2 respectively.In the structure of using spring eye 7d and helical spring 20 more than 2, can make the more miniaturization of diameter of helical spring 8, the front end 7b of certain blade 7 can be pressed on the roller 6 equably.
And, the end of the anti-blade-side of helical spring 20 is contacted with the cylinder inner wall 1a of seal container 1, and the bottom is set, makes the contacted structure in anti-blade-side end of helical spring 20 can obtain identical effect yet in the cylinder inner wall 1a side of the seal container 1 of blade groove 4a.
And, because what use on spring mechanism 8 is simple shape, cheap helical spring 20, so can reduce cost and assemble easily.
In this example, what use on spring mechanism 8 is helical spring 20, self-evident, even if also can obtain identical effect with the replacement of elastomers such as resin, gas.
In this example, just use 2 spring eye 7d and helical spring 20 to be illustrated respectively, but not limited, also be applicable to the situation of using 1 spring eye 7d and helical spring 20 respectively.
In addition, in this example, only need process and be provided with the spring eye 7d of degree of depth 1vna of the represented scope of inequality of formula 2 at the back side of blade 7 7a, be easy to realize, therefore can obtain described effect with cheap cost.
[example 2]
Below consulting accompanying drawing describes with regard to the 2nd example of the present invention.
Fig. 3 is near the transverse sectional view of blade groove of the compression mechanical part of rotary compressor in the invention process form 2.The front end of shown in Figure 3 is blade is pressed into to the state of the cylinder inner wall face of cylinder.
Different with the 1st example is, with the cylinder inner wall 1a place of the contacted seal container 1 in the end of helical spring 20 for the point of helical spring guide mechanism 1b is set.Helical spring guide mechanism 1b is made of the columned protuberance of diameter less than the internal diameter of the helical spring 20 at the cylinder inner wall 1a place that is arranged on seal container 1.That is, as can be seen from Figure 3, present the state that penetrates helical spring 20 inside as the columned protuberance of helical spring guide mechanism 1b.
In addition, the degree of depth 1vna of the spring eye 7d that is shorter in length than blade 7 of the helical spring guide mechanism 1b of the cylinder inner wall 1a of seal container 1 structurally.
The structure of example 2 is all identical with example 1, self-evident except that described structure, can obtain the same effect that is produced by these structures.
The effect that said structure is drawn then is described.
Because the helical spring guide mechanism 1b at the spring eye 7d of blade 7 and the cylinder inner wall 1a place of seal container 1; the two end part of helical spring 20 are except towards flexible direction; its motion is fixed; therefore; when helical spring 20 is flexible repeatedly; can prevent to block between the inlet of the spring eye 7d on the back side 7a of helical spring 20 and blade 7, can prevent to guarantee the reliability of rotary compressor because of helical spring 20 is deviate from, the caused fault of bending.Intake section at spring eye 7d also can add fillet R.Like this, owing to add fillet R, can further reduce between the inlet of the spring eye 7d on the back side 7a of helical spring 20 and blade 7 and block at the intake section of spring eye 7d.
In addition, because the length of the helical spring guide mechanism 1b of the cylinder inner wall 1a of seal container 1 is below the degree of depth 1vna of the spring eye 7d of blade 7, therefore, even when the approaching situation of the cylinder inner wall 1a of the back side of blade 7 7a and seal container 1, the front end of the bottom of spring eye 7d and helical spring guide mechanism 1b can not collide yet.Therefore, can set gap 1cr between the cylinder inner wall 1a of the back side 7a of blade 7 and seal container 1, in this example, can bring into play the effect of the 1st example of the present invention to greatest extent by inferior limit.
In addition, owing to be provided with helical spring guide mechanism 1b at the inboard inwall 1a place of seal container 1, structurally can not interfere with helical spring 20 and blade 7,1b is fixed on the supporting portion of using on the seal container 1 with the helical spring guide mechanism, be fixed on the supporting portion of using on the cylinder 4 with setting and compare, can add the sealing surface of linear leaf 7.
And small-sized rotary compressor generally uses the following blade 7 of the above 3.5mm of width 3.0mm, and the stroke of blade 7 is below the above 5.0mm of 3.0mm.In small-sized like this rotary compressor, considered the crush pad of helical spring 20 and used helical spring 20 more than the free length 10.0mm.In addition, general, by the helical spring 20 that steel, piano wire form, its two ends are fixed, when helical spring average diameter divided by helical spring free length, aspect ratio under the condition 5 below, produce the danger reduction of bending.Therefore, the diameter by making helical spring 20 can be guaranteed the reliability of rotary compressor more than the 2.0mm, below the width of blade 7.
In addition, carbon dioxide as working fluid, compare with other working fluids such as freon, replacement fluorine Leon, hydrocarbon, ammonias, the pressure height, the leakage of the working fluid between the gap of blade groove 4a and blade 7 is bigger, use example of the present invention, because the length of blade 7 is than length, so can reduce the leakage of working fluid in the past.
Especially, bigger as the density of the carbon dioxide of working fluid, the volume of cylinder of comparing with other working fluid also can reduce.That is,,,, can make compression mechanical part 2 further miniaturizations, so can realize the miniaturization of rotary compressor owing to used the present invention so volume of cylinder is diminished owing to use carbon dioxide as working fluid.
Like this according to this example, by as mentioned above as can be known, the invention provides rotary compressor a kind of simple structure, the small-sized efficient rate, owing in the spring eye 7d of the back side of blade 7 7a, can hold the part of spring 20 at least, therefore the space more than the crush pad that does not need required in the past helical spring 20 between blade 7 and the seal container 1 can add the seal length of linear leaf 7 and blade groove 7a.
The possibility of utilizing on the industry
Compressor involved in the present invention has the function of compression, carrying working fluid, can be used as in freezing The refrigerant such as refrigerator, air conditioner heat pump machine. In addition, also can be applied to vavuum pump etc.
Claims (7)
1. a rotary compressor has: seal container; Be arranged in described seal container inside, be provided with the cylinder of blade groove; Be provided with the bent axle of eccentric part; The roller that can be engaged in the described eccentric part of described bent axle freely to rotate, carry out eccentric rotation motion in described cylinder interior; The blade that in described blade groove, moves back and forth when being arranged in the described blade groove of described cylinder the preceding end in contact with described roller; Described blade is pressed on spring mechanism on the described roller, it is characterized in that, described blade, be provided with spring eye at described blade with the contacted opposition side of described roller, offering described spring eye in the cross section of the described blade vertical with the vibration-direction of described blade, is a part of holding described spring mechanism at least.
2. rotary compressor as claimed in claim 1 is characterized in that, has a plurality of described spring mechanisms, and described blade has described a plurality of spring eye, accommodates the part of described spring mechanism in described each spring eye at least respectively.
3. rotary compressor as claimed in claim 1 is characterized in that, described spring mechanism is a helical spring.
4. rotary compressor as claimed in claim 3 is characterized in that, a described helical spring end is housed inside in the described spring eye of described blade, is provided with the helical spring guide mechanism with the contacted base of the described helical spring the other end.
5. rotary compressor as claimed in claim 4 is characterized in that, described helical spring guide mechanism is arranged on the inner side surface of described seal container.
6. rotary compressor as claimed in claim 3, it is characterized in that, the width of described blade is below the above 3.5mm of 3.0mm, the reciprocating stroke of described blade is below the above 5.0mm of 3.0mm, described helical spring diameter is that 2.0mm is above and less than the width of described blade, and described helical spring free length is below 5 times of diameter.
7. rotary compressor as claimed in claim 1 is characterized in that, working fluid is a carbon dioxide.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP359745/2002 | 2002-12-11 | ||
| JP2002359745 | 2002-12-11 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1692228A true CN1692228A (en) | 2005-11-02 |
Family
ID=32500954
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2003801004211A Pending CN1692228A (en) | 2002-12-11 | 2003-11-17 | Rotary compressor |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20050214151A1 (en) |
| EP (1) | EP1500820A4 (en) |
| JP (1) | JPWO2004053335A1 (en) |
| KR (1) | KR20050084781A (en) |
| CN (1) | CN1692228A (en) |
| WO (1) | WO2004053335A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109026699A (en) * | 2018-08-21 | 2018-12-18 | 珠海凌达压缩机有限公司 | A kind of manufacturing method of the pump housing, compressor and the pump housing |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060140791A1 (en) * | 2004-12-29 | 2006-06-29 | Deming Glenn I | Miniature rotary compressor, and methods related thereto |
| DE102015217922A1 (en) * | 2015-09-18 | 2017-03-23 | Continental Automotive Gmbh | Method and two-part tool assembly for manufacturing a stator for an electric machine |
| DE102015217936A1 (en) * | 2015-09-18 | 2017-03-23 | Continental Automotive Gmbh | Method and one-piece tool assembly for manufacturing a stator for an electric machine |
| JP6305471B2 (en) * | 2016-07-25 | 2018-04-04 | 本田技研工業株式会社 | Stator manufacturing method and apparatus |
| KR20240071008A (en) | 2022-11-15 | 2024-05-22 | 주식회사 비에이치다온 | Ultrapure water production bubbler for cleaning semiconductor devices |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS50124204A (en) * | 1974-03-18 | 1975-09-30 | ||
| JPS51159010U (en) * | 1975-06-12 | 1976-12-17 | ||
| JPS56157394U (en) * | 1980-04-25 | 1981-11-24 | ||
| JPS57193089U (en) * | 1981-05-29 | 1982-12-07 | ||
| GB2111595B (en) * | 1981-12-04 | 1985-11-06 | Ken Hsu Song | A rotary gas compressor |
| US4598559A (en) * | 1985-05-31 | 1986-07-08 | Carrier Corporation | Reversible fixed vane rotary compressor having a reversing disk which carries the suction port |
| JP2000170677A (en) * | 1998-12-02 | 2000-06-20 | Matsushita Electric Ind Co Ltd | Rotary compressor |
| JP3579324B2 (en) * | 2000-03-30 | 2004-10-20 | 三洋電機株式会社 | Multi-stage compressor |
-
2003
- 2003-11-17 JP JP2004558395A patent/JPWO2004053335A1/en not_active Withdrawn
- 2003-11-17 KR KR1020047016443A patent/KR20050084781A/en not_active IP Right Cessation
- 2003-11-17 WO PCT/JP2003/014555 patent/WO2004053335A1/en not_active Application Discontinuation
- 2003-11-17 CN CNA2003801004211A patent/CN1692228A/en active Pending
- 2003-11-17 US US10/514,691 patent/US20050214151A1/en not_active Abandoned
- 2003-11-17 EP EP03772798A patent/EP1500820A4/en not_active Withdrawn
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109026699A (en) * | 2018-08-21 | 2018-12-18 | 珠海凌达压缩机有限公司 | A kind of manufacturing method of the pump housing, compressor and the pump housing |
| CN109026699B (en) * | 2018-08-21 | 2024-03-29 | 珠海凌达压缩机有限公司 | Pump body, compressor and manufacturing method of pump body |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1500820A1 (en) | 2005-01-26 |
| JPWO2004053335A1 (en) | 2006-04-13 |
| WO2004053335A1 (en) | 2004-06-24 |
| EP1500820A4 (en) | 2005-05-11 |
| US20050214151A1 (en) | 2005-09-29 |
| KR20050084781A (en) | 2005-08-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN1077658C (en) | Vortex fluid machinery | |
| CN100540901C (en) | Rotary compressor and use the refrigerating circulatory device of this rotary compressor | |
| CN1828057A (en) | Capacity-changing unit of orbiting vane compressor | |
| CN1789710A (en) | Hermetic compressor | |
| CN1692228A (en) | Rotary compressor | |
| CN1256514C (en) | Rotary compressor | |
| CN1906414A (en) | Hermetic compressor | |
| CN1788164A (en) | Rotary compressor | |
| CN2769556Y (en) | Vortex compressor | |
| CN111946584A (en) | A kind of compressor | |
| CN1018374B (en) | Fluid compressor | |
| CN1888435A (en) | Working oil supply structure for geared compressor | |
| CN1896531A (en) | Blade spring arrangement of rotary compressor | |
| CN212508689U (en) | A kind of compressor | |
| CN1916424A (en) | Exhaust structure of main bearing and rotation axis in revolve type compressor | |
| CN1118632C (en) | Fluid machinery | |
| CN1751183A (en) | Scroll compressor | |
| CN1363777A (en) | Silencer of exhaust valve for sealed rotary compressor | |
| CN2844511Y (en) | Buffle connecting structure of rotating-style rotor compressor | |
| CN1888433A (en) | Rotation type compressor | |
| CN1187587A (en) | Fluid compressor | |
| CN1289822C (en) | Oil supply device of vortex compressor | |
| CN1955472A (en) | Friction reducing structure of blade rotary compressor | |
| CN1746506A (en) | Double volume rotary compressor | |
| CN1510308A (en) | Rotary compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication |