CN101680447A

CN101680447A - Scroll type fluid machine

Info

Publication number: CN101680447A
Application number: CN200880018220A
Authority: CN
Inventors: 东山彰良
Original assignee: Sanden Corp
Current assignee: Sanden Corp
Priority date: 2007-05-31
Filing date: 2008-05-21
Publication date: 2010-03-24
Also published as: EP2154375A4; WO2008149672A1; JP2008297977A; EP2154375A1

Abstract

A scroll type fluid machine (1) has a root section (58) and a chamfered section (68). The root section (58) has a tapered surface (60) tilting from a tapered end (60a) located on a side face (44a) ofa wrap (44) toward an end plate surface (40a) upstanding on the wrap (44). The chamfered section (68) is formed on a wrap (42) paired with the wrap (44), which has the root section (58), and formed bychamfering the wrap (42) from a chamfered end (70) located on a side face (42a) of the wrap (42) toward a forward end surface (42b) of the wrap (42). The chamfered section (68) is formed in a size inwhich, when a slide surface (66) is formed, the chamfered section (68) is separated from the root section (58) and the distance from the chamfered end (70) to the slide surface (66) is greater than or equal to the distance from the tapered end (60a) to the slide surface (66).

Description

Convolute-hydrodynamic mechanics

Technical field

The present invention relates to a kind of convolute-hydrodynamic mechanics, relate in particular to a kind of convolute-hydrodynamic mechanics that is applicable to refrigerating and air-conditioning and heat pump water heater.

Background technique

This kind convolute-hydrodynamic mechanics, for example closed type scroll compressor rotate with respect to the static vortex disk revolution in the enclosure by movable orbiting scroll and move suction, the compression of implementation fluid (to call refrigeration agent in the following text) and discharge a series of flow process.

Specifically, panelling (Japanese: uprightly be provided with spiral helicine clinch (lap) on paneling runner plate) respectively at movable orbiting scroll and static vortex disk, these clinchs complement each other to form pressing chamber, implement above-mentioned a series of flow process by the volume that reduces this pressing chamber.In addition, the technology that the front end of clinch is carried out chamfered edge processing is well-known (for example the real clear 62-76185 communique, Japan Patent spy opened of Japan Patent opened 2001-329972 communique, Japan Patent spy and opened that 2004-76629 communique, Japan Patent are real opens clear 62-82391 communique).

Clinch generally utilizes cutting tools such as end mill to form by cutting.At this moment, cutting tool is aging, its front end produces when wearing and tearing, and the wear extent of the corresponding cutting tool of the root of clinch forms taper.

But, in above-mentioned each prior art, for not considering that it is bad to exist clinch to contact with each other thus because the machining error of the root of the clinch that the wearing and tearing of above-mentioned cutting tool cause is special, the leakage of refrigerant that flows out from pressing chamber increases the problem that the volumetric efficiency of compressor is low.

Summary of the invention

The present invention does in view of above-mentioned technical problem, and its purpose is to provide a kind of can preventing to increase and improve the convolute-hydrodynamic mechanics of the volumetric efficiency of fluid machinery owing to be formed at the clinch of movable orbiting scroll and the static vortex disk bad leakage of refrigerant amount that causes that contacts with each other.

For achieving the above object, technological scheme 1 described convolute-hydrodynamic mechanics comprises static vortex disk and movable orbiting scroll in the enclosure, this static vortex disk and movable orbiting scroll uprightly are provided with spiral helicine clinch respectively on the paneling of panelling, by movable orbiting scroll with respect to the static vortex disk revolution motion that rotates, the paneling sliding contact of the front-end face of clinch and paired clinch and form sliding contact surface, this a succession of flow process is discharged in being drawn into of implementation fluid, it is characterized in that, comprise: root, the clinch that it is formed at any one party in movable orbiting scroll and the static vortex disk or both sides has the conical surface that tilts towards the paneling that uprightly is provided with this clinch from the conical surface end that is positioned at this clinch side; And, chamfered edge portion, it is formed at and the paired clinch of clinch with root, from the chamfered edge end that is positioned at this clinch side towards the front-end face chamfered edge of this clinch and form, chamfered edge portion forms following size: along with the formation of sliding contact surface, chamfered edge portion and root portion from, and the distance from the chamfered edge end to sliding contact surface is more than the distance from conical surface end to sliding contact surface.

In the above-mentioned convolute-hydrodynamic mechanics, chamfered edge portion forms and the hands-off size of the root of paired clinch, along with the formation of sliding contact surface, can make clinch side each other butt reliably.Therefore, even if because the wearing and tearing of cutting tool such as end mill and form the conical surface during cutting clinch at the root of clinch, also can prevent because the increasing of the leakage of refrigerant amount that causes of clinch bad connection each other, and can improve the volumetric efficiency of fluid machinery.

As preferred embodiment, in the used heat utilized device of above-mentioned internal-combustion engine, root also has carry out the curved surface that rounding forms, the rounding end is positioned at this paneling from the conical surface to the paneling, chamfered edge portion has the second chamfered edge end on front-end face, and form following size: along with the formation of sliding contact surface, chamfered edge portion and root portion from, and the distance from the second chamfered edge end to the side of the clinch with this root is for more than the distance from the rounding end to this side.

According to this structure, even if except that the conical surface, also form curved surface, also can prevent increasing of leakage of refrigerant amount that clinch bad connection each other causes at the root of clinch, can further improve the volumetric efficiency of fluid machinery.

As preferred embodiment, in the used heat utilized device of above-mentioned internal-combustion engine, chamfered edge portion is with the formation of sliding contact surface, and the chamfered edge end is positioned at the position of conical surface end, and the second chamfered edge end is positioned at the position of rounding end.

According to this structure, can reduce and chamfered edge portion that the formation of pressing chamber is irrelevant and the clearance volume between root, promptly reduce the dead band (dead volume) between clinch, prevent increasing of the leakage of refrigerant amount that flows out from pressing chamber by the dead band, therefore can further improve the volumetric efficiency of fluid machinery.

As preferred embodiment, in the used heat utilized device of above-mentioned internal-combustion engine, chamfered edge portion is formed by the conical surface group more than 2.

According to this structure, chamfered edge portion can more closely form with respect to root, therefore can further reduce the dead band, thereby can further improve the volumetric efficiency of fluid machinery.

As preferred embodiment, in the used heat utilized device of above-mentioned internal-combustion engine, chamfered edge portion comprises circular-arc portion.

According to this structure, chamfered edge portion can more closely form with respect to root, therefore can reduce the dead band as far as possible, thereby can further improve the volumetric efficiency of fluid machinery.

As preferred embodiment, in the used heat utilized device of above-mentioned internal-combustion engine, working fluid is the refrigeration agent that is formed by carbon dioxide.

According to this structure, compare with the situation of using other refrigeration agents, because fluid machinery moves in high pressure more, at a high speed rotary area, so the leakage of refrigerant amount may increase, and will be more remarkable but utilize the raising effect of volumetric efficiency of the fluid machinery of said structure.

Description of drawings

Fig. 1 is the longitudinal section of the closed type scroll compressor of expression first embodiment of the invention.

Fig. 2 is the figure that amplifies the chamfered edge portion of expression first embodiment of the invention.

Fig. 3 is the figure that amplifies the chamfered edge portion of expression second embodiment of the invention.

Embodiment

Below, the accompanying drawings one embodiment of the present invention.

At first, first mode of execution is described.

Fig. 1 represents the closed type scroll compressor as an example of the fluid machinery of embodiment of the present invention.This compressor 1 is assembled in the refrigerating circuit of refrigerating air conditioning device and heat pump water heater etc.This refrigerating circuit comprises the carbon dioxide coolant circuit path as an example of working fluid, and compressor 1 sucks refrigeration agent from path, and its compression back is discharged towards path.

This compressor 1 comprises shell 2, loam cake 6, lower cover 8 is arranged in that upside, the downside of the main part 4 of shell 2 are chimeric airtightly respectively, and thus, the inside of main part 4 is sealed, and the head pressure of refrigeration agent works.On the appropriate location of main part 4, be connected with the suction pipe 10 of suction, on the appropriate location of loam cake 6, be connected with the discharge tube 12 that the compressed refrigerant in the shell 2 is sent to above-mentioned loop from the refrigeration agent of above-mentioned loop introducing.

Contain motor 14 in main part 4, dispose rotating shaft 16 in this motor 14, rotating shaft 16 is by being driven to motor 14 energisings.In addition, the upper end side of rotating shaft 16 is supported to and can rotates freely by main shaft frame 18 by bearing, and this main shaft frame 18 is fixed with shell 2 one.

On the other hand, the lower end side of rotating shaft 16 is supported to and can rotates freely by countershaft frame 20 by bearing.In addition, in the lower end side of rotating shaft 16 oil pump 22 is installed, oil pump 22 attracts to be formed at the lubricant oil in the accumulator 24 of lower cover 8 inboards.This lubricant oil runs through and rises in the fuel feeding road 26 that forms along axial direction in rotating shaft 16, supplies to motor 14 and vortex element 28 etc. from the upper end of rotating shaft 16, plays lubricated, and the effect of the sealing of slip surface of each sliding parts and bearing etc.At this moment, the head pressure of refrigeration agent also promotes the rising of the lubricant oil in the fuel feeding road 26 to the effect of the lubricant oil pasta of accumulator 26.In addition, be formed with the introducing port 30 of lubricant oil on the appropriate location of countershaft frame 20, the lubricant oil that supplies to each sliding parts in the compressor 1 is stored into accumulator 24 by introducing port 30.

Said units 28 is configured in the top of the motor 14 in the main part 4, implements suction, the compression of refrigeration agent and discharges this a succession of flow process.

Specifically, this unit 28 is made of movable orbiting scroll 34 and static vortex disk 36, movable orbiting scroll 34 comprises panelling 38, on the paneling 38a of this panelling 38, uprightly be provided with the helical clinch 42 that the panelling 40 towards static vortex disk 36 extends, on the paneling 40a of the panelling 40 of static vortex disk 36, also uprightly be provided with the helical clinch 44 that extends towards panelling 38.

In addition, these

clinch

42,44 mutual interlocks suck refrigeration agent from the space of panelling 38 outer circumferential sides and the suction chamber that is communicated with suction pipe 10, form pressing chamber.With respect to the static vortex disk 36 revolution motion that rotates, pressing chamber moves towards the center and reduces its volume from the outer radial periphery side of these

clinchs

42,44 by movable orbiting scroll 34.

For making the motion that rotates of revolving round the sun of above-mentioned movable orbiting scroll 34, be formed with axle sleeve 46 in the back side of panelling 38, this axle sleeve 46 by bearing by and the integrally formed eccentric shaft of the upper end side of rotating shaft 16 be supported to and can rotate freely.In addition, the rotation of movable orbiting scroll 34 is stoped pin to stop by not shown rotation.

On the other hand, static vortex disk 36 is fixed in main shaft frame 18, and panelling 40 separates pressing chamber side and discharge chamber 50 sides.On the appropriate location of the middle body of static vortex disk 36, the tap hole 52 that is communicated with the pressing chamber side is located at panelling 40 with connecting, and this tap hole 52 is configured in expulsion valve 54 switchings of discharge chamber 50 sides of static vortex disk 36.In addition, comprise that discharge chamber 50 sides of the static vortex disk 36 of expulsion valve 54 are discharged from top 56 coverings, the noise when utilizing these discharge top 56 inhibition expulsion valves 54 to open.

In the above-mentioned compressor 1, along with the rotation of rotating shaft 16, movable orbiting scroll 34 not from then the motion that rotates of revolving round the sun.The revolution of this movable orbiting scroll 34 motion that rotates will suck the inside of unit 28 and compression unit 28 in from suction chamber by the refrigeration agents that suction pipe 10 is introduced in the main parts 3, and afterwards, the refrigeration agent after this is compressed is from tap hole 52 discharges.In addition, the refrigeration agent of discharging from the tap hole 52 arrival discharge chamber 50, back of circulate shell 2 in is delivered to outside the compressor 1 by discharge tube 12.

Shown in the enlarged view of the

clinch

42,44 of Fig. 2, clinch 44 has the root 58 continuous with paneling 40a on the 44a of its side.Root 58 is to form in the stage that cutting tools such as utilizing end mill carries out the cutting of clinch 44, is made of the conical surface 60 and curved surface 62.

The conical surface 60 carries out bevel with respect to the axial direction of static vortex disk 36 with the tilt angle A of regulation towards paneling 40a side from the terminal 60a of the conical surface that is positioned at side 44a and forms.The degree of wear of the end mill front end that the position of the terminal 60a of the conical surface and tilt angle A use during according to cutting etc. is determined, use without exception the end mill of regulation pattern and preestablish when changing frequency, can predict the position of the terminal 60a of the conical surface and the deviation range of tilt angle A to a certain extent according to the behaviour in service of end mill.

On the other hand, curved surface 62 carries out rounding to paneling 40a with the radius r of regulation from the boundary point 60b as the border of itself and the conical surface 60 and processes, and the terminal 62a of the rounding of curved surface 62 is positioned on the paneling 40a.That is, curved surface 62 is connected paneling 40a smoothly with the circular arc of the conical surface 60 with radius r.

Relative therewith, clinch 42 is formed with front end 64 from its side 42a to front-end face 42b, when movable orbiting scroll 34 revolution rotates motion, and front-end face 42b and paneling 40a sliding contact and form sliding contact surface 66.

At this, on front end 64, be formed with chamfered edge portion 68, chamfered edge portion 68 to front-end face side conical surface end (the second chamfered edge end) 72 chamfered edges that are positioned at front-end face 42b, forms the conical surface 74 from the side conical surface end (chamfered edge end) 70 that is positioned at side 42a.

In addition, this conical surface 74 is along with the formation of sliding contact surface 66, side conical surface end 70 is positioned on the axial direction of movable orbiting scroll 34 position of the above distance in position of terminal 60a from paneling 40a to the conical surface, and front-end face side conical surface end 72 position from the side 44a of clinch 44 to the above distance in position of the terminal 62a of rounding upwards, footpath that is positioned at movable orbiting scroll 34.

Promptly, in the present embodiment, on the deviation range of the tilt angle A of the position of the terminal 60a of the conical surface of root 58 places of considering clinch 44 in advance prediction and the conical surface 60, form chamfered edge portion 68 bigger, in order to avoid its with root 58, be the conical surface 70 and curved surface 62 interference.Thus, when movable orbiting scroll 34 revolution rotated motion, along with the formation of sliding contact surface 66, side 42a, the 44a that can make

clinch

42,44 be butt reliably each other.Therefore, even if the front end of cutting tool such as end mill wearing and tearing and on the root 58 of the clinch 44 that processes, form the conical surface 60 during cutting clinch 44, increasing of the leakage of refrigerant amount that flows out from pressing chamber that clinch 42 causes with respect to the bad connection of clinch 44 also can prevent owing to can improve the volumetric efficiency of compressor 1.

At this, shown in the dotted line among Fig. 2, in processing clinch 44 back to clinch 42 processing or reprocessing, when transforming etc., if can pre-determine position and the tilt angle A of the terminal 60a of the conical surface, then preferably chamfered edge portion 68 is formed: along with the formation of sliding contact surface 66, side conical surface end 70 is positioned at the position of the terminal 60a of the conical surface, and front-end face side conical surface end 72 is positioned at the position of the terminal 62a of rounding.At this moment, can reduce and the movable clinch 42 that the formation of pressing chamber is irrelevant and the fixing volume in the gap 76 of 44 of clinchs, that is, reduce dead band V.

Because the pressure of dead band V is in a ratio of low pressure with pressure in the pressing chamber, so dead band V means that greatly the volume that holds the leakage of refrigerant that flows out from pressing chamber in the unit 28 increases, and becomes the main cause of the leakage of refrigerant amount increase of flowing out from pressing chamber.Therefore, can get rid of this main cause, further improve the volumetric efficiency of compressor 1 by the reduction dead band.

Then, second mode of execution is described.

As shown in Figure 3, the chamfered edge portion 78 of this second mode of execution is formed by first conical surface and second conical surface (conical surface group) 80,82, because other adopt and the identical structures of above-mentioned first mode of execution, so main the point different with above-mentioned mode of execution 1 is described.

First conical surface 80 side conical surface end 70 from the side carries out bevel with respect to the axial direction of static vortex disk 36 with fixing tilt angle A1 towards front-end face 42b side and forms, on the other hand, second conical surface 82 carries out bevel from first conical surface 80 and boundary point 80a second conical surface 82 to front-end face side conical surface end 72 with the tilt angle A2 of regulation and forms.Promptly, chamfered edge portion 78 is under sliding contact surface 66 established states, formation is 2 sections conical surface shapes of convex towards root 58, is that tilt angle A1 is configured to the tilt angle A greater than the conical surface 60 at least, and tilt angle A2 is configured to that boundary point 80a does not contact with root 58 and the size of separating.

At this, among Fig. 3, chamfered edge portion 78 forms: along with the formation of sliding contact surface 66, side conical surface end 70 is positioned at the position of the terminal 60a of the conical surface, and front-end face side conical surface end 72 is positioned at the position of the terminal 62a of rounding, but side conical surface end 70 is positioned on the axial direction of movable orbiting scroll 34 position of the above distance in position of terminal 60a from paneling 40a to the conical surface at least, and front-end face side conical surface end 72 be positioned at movable orbiting scroll 34 the footpath upwards from the side 44a get final product to the position of the above distance in position of rounding end 62a.

So, identical with above-mentioned first mode of execution, in the compressor 1 that second mode of execution relates to, formation along with sliding contact surface 66, side 42a, the 44a that also can make

clinch

42,44 be butt reliably each other, prevent increasing of the leakage of refrigerant amount that flows out from pressing chamber, and improve the volumetric efficiency of compressor 1.

Especially in the situation of second mode of execution, compare, can further reduce dead band V, thereby can further improve the volumetric efficiency of compressor 1 with the chamfered edge portion 68 of first mode of execution.

In addition, chamfered edge portion 78 is not limited to 2 sections conical surface shapes, also can be under sliding contact surface 66 established states, formation is towards the multistage conical surface shape more than 3 sections that is convex of root 58, can further reduce dead band V this moment, thereby can improve to a nearlyer step volumetric efficiency of compressor 1, very desirable.

More than be the explanation of an embodiment of the present invention, but the present invention is not limited to the respective embodiments described above, can in the scope that does not break away from the technology of the present invention thought, carries out all changes.

For example, in the respective embodiments described above, front end 64 chamfered edges of clinch 42 become conical surface shape and multistage conical surface shape, but but for example also chamfered edge become when forming sliding contacting part 66 and be curved surface shape oval and circular arc (circular-arc portion) part towards root 58.In addition, also can use the shape of this kind conical surface and curved surface combination that front end 64 is carried out chamfered edge, this kind situation is with top identical, along with the formation of sliding contact surface 66, side 42a, the 44a that can make

clinch

42,44 be butt reliably each other, and can reduce dead band V as far as possible.Thus, play to prevent increasing of the leakage of refrigerant amount that flows out from pressing chamber reliably, and can increase substantially the effect of the volumetric efficiency of compressor 1.

In addition, in the respective embodiments described above, for being illustrated in the situation that forms formation chamfered edge portion on root and the clinch 42 on the clinch 44 of static vortex disk 36 at movable orbiting scroll 34, certainly, the present invention also can be applicable to forming root on the clinch 42 and form the situation of chamfered edge portion and the situation that forms root and chamfered

edge portion clinch

42,44 both sides on clinch 44 on the contrary.

In addition, use carbon dioxide as refrigeration agent in the respective embodiments described above, but be not limited to this.But, by using carbon dioxide as refrigeration agent, make movable orbiting scroll 34 rotate in the zone at high pressure, high speed rotating, compare with the situation of using other refrigeration agents, because equipment moves in high pressure more, at a high speed rotary area, therefore the leakage of refrigerant amount may increase, but utilizes said structure can prevent the problems referred to above, makes that the raising effect of volumetric efficiency of compressor 1 is more remarkable.

In addition, in the respective embodiments described above, be illustrated for the closed type scroll compressor in the refrigerating circuit that is assembled into refrigerating air conditioning device and heat pump water heater etc., but be not limited thereto, the present invention also can be applicable to convolute-hydrodynamic mechanics such as compressor beyond the closed type in various fields and decompressor.

Claims

1. convolute-hydrodynamic mechanics, it is characterized in that, comprise static vortex disk and movable orbiting scroll in the enclosure, the spiral helicine clinch of this static vortex disk and movable orbiting scroll uprightly is located at the paneling of panelling in couples respectively, by described movable orbiting scroll with respect to the described static vortex disk revolution motion that rotates, the described paneling sliding contact of the front-end face of one side clinch and opposite side clinch and form sliding contact surface, this a succession of flow process is discharged in being drawn into of implementation fluid, and described convolute-hydrodynamic mechanics comprises:

Root, this root are formed at a described side clinch at least, have the conical surface that tilts towards the described paneling that uprightly is provided with this clinch from the conical surface end of the side that is positioned at this clinch; And

Chamfered edge portion, this chamfered edge portion are formed at and have the paired opposite side clinch of described at least one side clinch of described root, and the described front-end face from the chamfered edge end that is positioned at this clinch side to this clinch carries out chamfered edge and forms,

Described chamfered edge portion forms following size: along with the formation of described sliding contact surface, described chamfered edge portion and described root portion from, and the distance from described chamfered edge end to described sliding contact surface is to more than the distance of described sliding contact surface from described conical surface end.

2. convolute-hydrodynamic mechanics as claimed in claim 1 is characterized in that,

Described root also has curved surface, and this curved surface carries out rounding from the described conical surface to described paneling and forms, and the rounding end is positioned at this paneling,

Described chamfered edge portion has the second chamfered edge end on described front-end face, and, described chamfered edge portion forms following size: along with the formation of described sliding contact surface, described chamfered edge portion and described root portion from, and the distance from the described second chamfered edge end to the described side of described clinch with this root for from described rounding end to more than the distance of this side.

3. convolute-hydrodynamic mechanics as claimed in claim 2 is characterized in that, described chamfered edge portion is with the formation of described sliding contact surface, and described chamfered edge end is positioned at the position of described conical surface end, and the described second chamfered edge end is positioned at the position of described rounding end.

4. as each described convolute-hydrodynamic mechanics in the claim 1 to 3, it is characterized in that described chamfered edge portion is formed by the conical surface group more than 2.

5. as each described convolute-hydrodynamic mechanics in the claim 1 to 4, it is characterized in that described chamfered edge portion comprises circular-arc portion.

6. as each described convolute-hydrodynamic mechanics in the claim 1 to 5, it is characterized in that described working fluid is the refrigeration agent that is formed by carbon dioxide.