CN100439708C - Fluidmaschine - Google Patents
Fluidmaschine Download PDFInfo
- Publication number
- CN100439708C CN100439708C CNB2006100043375A CN200610004337A CN100439708C CN 100439708 C CN100439708 C CN 100439708C CN B2006100043375 A CNB2006100043375 A CN B2006100043375A CN 200610004337 A CN200610004337 A CN 200610004337A CN 100439708 C CN100439708 C CN 100439708C
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- China
- Prior art keywords
- housing
- overcoat
- shell
- fluid machinery
- cylinder part
- 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.)
- Expired - Fee Related
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/121—Casings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/02—Light metals
- F05C2201/021—Aluminium
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
The present invention provides a fluid machine having a housing with light weight and high strength and excellent in weatherability. A compressor 4 as a fluid machine has a housing 12 housing a compression unit compressing CO2 refrigerant as working fluid and a drive unit transmitting power from a rotational shaft 30 to the compression unit. A casing 14 of the housing 12 is made of steel material, and its large diameter cylinder part 16 and inclined cylinder part 20 surround an outer peripheries of the compression unit and the drive unit. A shell 78 made of aluminum material is disposed only to outer peripheral faces of the large diameter cylinder part 16 and the inclined cylinder part 20.
Description
Technical field
The present invention relates to a kind of fluid machinery.
Background technique
In recent years, wish to compare the CO that more helps environment with a kind of with traditional fluorocarbon refrigerants
2Refrigeration agent substitutes the refrigeration agent that is used for refrigerating circuit, has therefore developed various technology for the fluid machinery of the compressor that is used for this refrigerating circuit.
For example disclose a kind of shell that is used for compressor that is disclosed among the 2004-218585 in Japanese unexamined patent, this shell also is included in an iron housing in the inboard or the outside of aluminium casing.Using CO
2Under the situation of refrigeration agent, the refrigerant pressure in the compressor will be elevated to pressure high when using fluorocarbon refrigerants.Yet, in this compressor, think that the double layer construction of aluminium shell and iron shell is suitable for this shell, shell just can be done gentlyer like this, and the intensity of shell also is guaranteed.
Yet, in the shell of above-mentioned prior art compressor, bring such problem at the arranged outside iron shell of aluminum inner casing, promptly shell to external world the resistivity of environment weaken.This is owing to get rusty easily at the iron shell that places the outside, and intensity is descended owing to getting rusty.In addition, the coefficient of linear expansion of aluminum inner casing is greater than the coefficient of linear expansion of iron shell, and when compressor operating, the temperature of aluminum inner casing will be than the temperature height of the iron shell outside it.Therefore, when compressor operating, the thermal expansion of aluminum inner casing is bigger than the thermal expansion of iron shell, but the thermal expansion of aluminum inner casing always connects mutually with the iron shell of tight contact in its outside, like this, because stress is concentrated, the aluminium shell that intensity is lower than iron shell just might break.
On the other hand, in the shell of above-mentioned prior art compressor, the housing parts of forming cylinder head also is a double layer construction.It is less that suction chamber in the cylinder head and the inner surface area of pressing chamber are compared with the inner surface area of crank chamber, even the pressure in suction chamber and the pressing chamber is owing to adopted CO
2Refrigeration agent and rising does not adopt double layer construction again simultaneously, and the intensity of cylinder head also can be guaranteed.Yet, in such compressor, the housing parts of forming cylinder head has also been adopted double layer construction, thus the weight of cylinder head, and promptly the overall weight of compressor increases.
Summary of the invention
An object of the present invention is to provide a kind of fluid machinery, the shell that this fluid machinery has is in light weight, intensity is high and weather resistance is strong.
In order to achieve the above object, fluid machinery of the present invention is characterised in that this shell comprises: an overcoat, and this overcoat surrounds the external peripheral surface of a compression unit and a driver element and made by iron; And a housing, this housing only is formed on an external peripheral surface of overcoat and is made by alumina-base material.
In fluid machinery of the present invention, the overcoat that the external peripheral surface of compression unit and driver element surrounds is made by iron, and had enough intensity and use for example CO
2Refrigeration agent is as working fluid.
In addition, in this fluid machinery, a housing only is located on the external peripheral surface of the overcoat that the external peripheral surface of compression unit and driver element is surrounded.Therefore, in this fluid machinery, can limit that owing to housing is set weight is increased, and can manage to reduce weight.
Therefore in addition, in fluid machinery of the present invention, this housing is made by alumina-base material, can prevent the generation of getting rusty at the part place that overcoat is covered by housing, and the weather resistance of shell is improved also.
In addition, in fluid machinery of the present invention, on the external peripheral surface of the overcoat that iron is made, form the housing that an alumina-base material is made, and the overcoat that will reach the temperature that is higher than housing is used the iron of linear expansion coeffcient less than alumina-base material.Therefore, in this fluid machinery, can reduce the difference of the thermal expansion between overcoat and the housing, and in the process to its operation, acting on the stress that intensity is lower than on the housing of overcoat will diminish, thus the durability of housing, and therefore the durability of shell can be improved.
Like this, in fluid machinery of the present invention, its shell has lighter weight, higher intensity and higher weather resistance, is preferable for adopting CO2 as the automobile air-conditioning refrigeration loop of refrigeration agent therefore.
As preferable pattern, one compression unit comprises a cylinder seat and inserts a piston in the cylinder barrel of cylinder seat, one driver element comprise can be provided with a swash plate of running shaft one rotation and with piston, rotatablely moving of swash plate converted to the reciprocating a pair of guide plate of piston, this shell comprises a cylinder head, this cylinder head is connected with overcoat and is made by alumina-base material, is used for supplying working fluid and working fluid is charged into compression unit.That is to say that in the situation of this pattern, fluid machinery is an oblique tray type compressor, and except the overcoat that the external peripheral surface with compression unit and driver element surrounds, cylinder head also forms separative element.Therefore, make overcoat with iron easily, and only make cylinder head with alumina-base material.The result can easily make the weight saving of fluid machinery.
In addition, flow into the pressing chamber of cylinder head from the working fluid of compression unit, but because with the internal surface of driver element, be that the part that overcoat surrounds crank chamber is compared, the inner surface area of pressing chamber is less, therefore the intensity that any housing just can guarantee cylinder head need be set on the outer surface of cylinder head.
As a preferable pattern, housing has a mounting portion that is used to install fluid machinery.Under the situation of this pattern, in the housing that alumina-base material is made, can easily form the mounting portion and have higher mechanical precision.
Like this, this mounting portion can easily be formed in the housing, and has higher mechanical precision, so the mounting point of fluid machinery and mounting type thereof be subjected to the less-restrictive of the shape of mounting portion and layout etc., but also can reduce the manufacture cost of fluid machinery.In addition, under the mounting portion was formed on situation in the housing, the polytype fluid machinery that is used for multiple automobile by standardization, therefore can further reduce the manufacture cost of fluid machinery at overcoat.In addition, under this situation,, can reduce weight, simultaneously except casting, can also make overcoat with the method for punching press etc. because the shape of shell is simplified.For this reason, also can reduce cost for manufacturing compressor.
As a preferable pattern, this housing also has a radiating fin.Under the situation of this pattern, for the housing of making by alumina-base material, can easily form radiating fin, and have higher mechanical precision with complicated shape.In addition, because the radiating fin made by alumina-base material has thermal conductivity preferably, the heat that utilizes this radiating fin to generate in the release fluids machinery fast.Therefore but the heat in the limit fluid machinery rises, and can further improve its serviceability.
As a preferable pattern, use a mould of the overcoat of portion's placement within it to come cast housing.Under the situation of this pattern, compare with the situation that will be the respectively independent housing of making is fixed on the outer surface of overcoat, housing is fixed to the outer operation that puts will become simpler, simultaneously, tight contact performance between housing and the overcoat will be higher, thereby the intensity of shell will be higher also.In addition, closely the raising of contact performance can improve the thermal conductivity between housing and the shell, thereby improves the heat dissipating capacity of radiating fin.
Like this, housing is fixed to the outer operation that puts will become and be easier to, thereby can reduce the manufacture cost of fluid machinery.In addition, the outer cover intensity that has improved and the serviceability of fluid machinery is further enhanced by the heat dispersion that radiating fin improves.
As a preferable pattern, shell also comprises a sprayfused coating that is arranged between shell and the housing and is made by alumina-base material.Under the situation of this pattern, the tight contact performance between housing and the overcoat can become higher by sprayfused coating, thereby further improves the intensity of shell, and also is further enhanced by the hot release performance of radiating fin.As its result, the serviceability of fluid machinery will be further enhanced.
As a preferable pattern, shell has the coating in zone that formation does not have the external peripheral surface of covering shell on the coat.That is to say, need on the whole zone of overcoat external peripheral surface, a housing be set.Under the situation of this pattern, on the zone that does not have covering shell on the external peripheral surface of overcoat, be formed with a coating, thereby can prevent that this zone from getting rusty.As its result, the weather resistance of this fluid machinery can be guaranteed.
Description of drawings
Can more completely understand the present invention from following detailed description that provides and accompanying drawing, these accompanying drawings are schematically, because of rather than limitation of the invention, wherein:
Fig. 1 is the longitudinal section that the fluid machinery among the embodiment who is applied to refrigerating circuit is shown;
Fig. 2 is illustrated in the figure that is formed at the sprayfused coating between an overcoat and the housing in the fluid machinery of a modification in the mode of amplifying;
Fig. 3 is the longitudinal section that a fluid machinery in the modification is shown.
Embodiment
Fig. 1 shows a refrigerating circuit of forming a car air-conditioner part.
Refrigerating circuit is provided with uses CO
2(carbon dioxide) is equipped with compressor 4, gas cooler 6, expansion valve 8 and vaporizer 10 in turn as the circulating line 2 of refrigeration agent in circulating line 2.Compressor 4 compressed refrigerants and with its row to gas cooler 6, thereby refrigeration agent circulates in circulating line 2.
Compressor 4 as an embodiment's fluid machinery among Fig. 1 is called as displacement-variable swashplate compressor, and the shell 12 of compressor 4 comprises the overcoat of being made by iron 14.The shape of overcoat 14 is similar to the classification cylinder, and have than diameter cylinder part 16, divide 18 and inclined cylinder part 20 than the minor diameter cylinder part, inclined cylinder part external diameter between dividing 18 than diameter cylinder part 16 with than the minor diameter cylinder part reduces gradually.
The two ends of overcoat 14, promptly divide 18 outer end to open respectively than diameter cylinder part 16 with than the minor diameter cylinder part.Adaptive in the inner circumferential surface than diameter cylinder part 16 have a cylindrical cylinder seat 22, and this cylinder seat is positioned at than near diameter cylinder part 16 outer ends.Cylinder seat 22 is made by iron, and crank chamber 24 is spaced between dividing 18 at cylinder seat 22 with than the minor diameter cylinder part, and than diameter cylinder part 16 and inclined cylinder part 20 crank chamber 24 is surrounded.In addition, the zone that cylinder seat 22 is surrounded, promptly forming thicklyer, thereby forming thicker regional 26 than near the zone the outer end in the diameter cylinder part 16.In thicker regional 26, form a plurality of at the axial bore 28 than the outer Transverse plane upper shed of diameter cylinder part 16, tapping internal thread on the inner circumferential surface of each axial bore 28.
Running shaft 30 places in the overcoat 14, and running shaft 30 extends through crank chamber 24 along its axial direction.Running shaft 30 is rotatably mounted by bearing 32 and 34 by cylinder seat 22 and inclined cylinder part 20.
In addition, accommodate the ring-type swash plate 36 around running shaft 30 in crank chamber 24, swash plate 36 is installed on the running shaft 30 by leaning device 38.Therefore, swash plate 36 can rotate integratedly with running shaft 30, and can tilt against running shaft 30.In addition, leaning device 38 comprises can be with running shaft 30 rotor rotated 40 integratedly, and bearing 34 is arranged between the inner circumferential surface of the external peripheral surface at rotor 40 centers and inclined cylinder part 20.
On the other hand, the axis around running shaft 30 forms a plurality of concentric cylinder barrels 42 in cylinder seat 22.Cylinder barrel 42 is parallel with running shaft 30, but inserts piston 44 from crank chamber 24 to-and-fro motion ground in each cylinder barrel 42.The end of the piston 44 in charging into crank chamber 24 forms a sagging part to running shaft 30 openings, and the internal surface of the part of sinking forms spheric seat.In spheric seat, be equipped with a pair of hemispheric a pair of guide plate 48 that is respectively, and these guide plates 48 are clipped in the middle slidably from the both sides of thickness direction with the external peripheral surface of swash plate 36.
On the outer end face of cylinder head 52, form suction port 58 and floss hole (not illustrating in the drawings), and suction port 58 is connected with above-mentioned circulating line 2 with floss hole (not illustrating in the drawings).In addition, in cylinder head 52, divide to be separated with suction chamber 60 and pressing chamber 62, and suction chamber 60 links to each other with floss hole with suction port respectively with pressing chamber 62.In addition, in cylinder head 52, accommodate a solenoid electric valve (not illustrating in the drawings).By solenoidal opening, but this solenoid electric valve opening/closing is regulated traffic channel (not illustrating in the drawings) from the pressure that pressing chamber 62 extends to crank chamber 24.
In addition, suction chamber 60 is communicated with each cylinder barrel 42 by sucking pilot valve (not illustrating in the drawings), and on the other hand, suction chamber 60 is communicated with crank chamber 24 all the time by the fixed hole (not illustrating in the drawings) that is formed in the valve plate 50.In addition, by the discharging pilot valve of being made up of a guiding valve member (not illustrating in the drawings) and valve guard 64, pressing chamber 62 also is communicated with each cylinder barrel 42.
On the other hand, running shaft 30 has by mechanical sealing element 66 from divide 18 ends of stretching out 68 than the minor diameter cylinder part.Magnetic clutch 70 with drive wheel 69 is connected in an end 68 of running shaft 30, and magnetic clutch 70 by divide than the minor diameter cylinder part 18 by bearing 71 rotatably mounted.In this respect, ring support 72 is engaged in than the minor diameter cylinder part divides on the end of 18 side inclined cylinder part 20, the solenoid 74 of magnetic clutch 70 is fixed in inclined cylinder part 20 by support 72.Along with the on/off operation of solenoid 74, magnetic clutch 70 passes to running shaft 30 with power from motor 76 off and on.
Herein, will be arranged on the outer surface of above-mentioned shell 12 by the housing 78 that alumina-base material is made.Housing 78 and inclined cylinder part 20 with closely contact than diameter cylinder part 16 external peripheral surface separately, and on the outer surface of overcoat 14, cover preset thickness to support 72 from outer end than diameter cylinder part 16.Housing 78 has two and covers mounting portion 80 than the end of diameter cylinder part 16 in inclined cylinder part 20 sides, and from the circumferencial direction of shell 78, these ends are apart from one another by the angle of rotation of opening 180 °.The shape of mounting portion 80 is configured to cuboid, and is 78 parallel protruding along diametric(al) from housing respectively, and through hole 82 is formed near its central position.On the other hand, in cylinder head 52, also form, and this mounting portion 84 also has through hole 86 from the mounting portion 84 that its end wall stretches out.Compressor 4 for example is installed on the motor 76 by putting a bolt that passes these through holes 82 and 86.
The work of above-mentioned compressor 4 will be described below.
When magnetic clutch 70 is opened, be sent to running shaft 30 from the power of motor 76 by magnetic clutch 70, thereby make running shaft 30 rotations.The rotation of running shaft 30 is converted into the to-and-fro motion of piston 44 by swash plate 36, and a series of working procedure is carried out in the to-and-fro motion of each piston 44.This a series of working procedure comprises: the refrigeration agent in the suction chamber 60 is sucked suction process in the cylinder barrel 42 by sucking pilot valve; The compression process of the refrigeration agent in the compression cylinder tube 42; And the discharge process that compressed refrigeration agent is entered pressing chamber 62 by the discharging pilot valve.In addition, control pressure (back pressure) in the crank chamber 24 by the on/off operation of solenoid electric valve, thus the length of stroke of increase/minimizing piston 44, the discharge amount of the refrigeration agent that from compressor 4, gives off with regard to can regulate.
The overcoat 14 that is coated with cylinder seat 22 and crank chamber 24 in above-mentioned compressor 4 is made by iron, and is using for example CO
2Refrigeration agent has enough intensity as working fluid the time.
In addition, 4 on this compressor is provided with housing 78 on the outer surface than diameter cylinder part 16 and inclined cylinder part 20 that coats cylinder seat 22 and crank chamber 24.Therefore, in this compressor 4, be restricted owing to the shell 12 weight increases that housing 78 causes are set, and can reduce weight.
In addition, in this compressor 4, housing 78 is made by alumina-base material, therefore can prevent to get rusty at the part place that overcoat 14 is stamped housing 78, thereby improve the resistivity of environment to external world.
In addition, in this compressor 4,78 of the housings of being made by alumina-base material are formed on the outer surface of being made by iron than diameter cylinder part 16 and inclined cylinder part 20, and for will reach the temperature that is higher than housing 78 than diameter cylinder part 16 and inclined cylinder part 20, use linear expansion coeffcient to be lower than the iron of alumina-base material.Therefore, in this compressor 4, linear expansion coeffcient difference between than diameter cylinder part 16 and housing 78 and between inclined cylinder part 20 and housing 78 descends, and in its working procedure, be applied to intensity and be lower than than the pressure on the housing 78 of diameter cylinder part 16 and inclined cylinder part 20 and will become less.Therefore, in this compressor, the serviceability of the serviceability of housing 78 and housing 12 can be improved.
In addition, because this compressor 4 is an oblique tray type compressor, therefore make overcoat 14 with iron easily, and have only the manufacturing of cylinder head 52 usefulness alumina-base materials simultaneously.In addition, work as high pressure CO
2When refrigeration agent flows into the pressing chamber 62 of cylinder heads 52 from cylinder barrel 42, owing to compare with the inner surface area in being contained in crank chamber 24 than diameter cylinder part 16 parts, therefore the inner surface area of pressing chamber 62 is less, even also can guarantee the intensity of cylinder head 52 when shell not being set on the outer surface of cylinder head 52.
In addition, in this compressor 4, the mounting portion 80 and 84 that is used to install shell 12 is the cylinder head 52 that is arranged at housing 78 integratedly and is made by alumina-base material, so mounting portion 80 and 84 can easily form, and mechanical precision is higher.Therefore, not only the mounting point of compressor 4 and installation method thereof are subjected to the less-restrictive of the shape and the layout of mounting portion 80 and 84, and the manufacture cost of compressor 4 also can reduce.In addition, under mounting portion 80 was formed on situation in the shell 78, the polytype compressor that is used for multiple automobile by standardization, therefore can further reduce the manufacture cost of compressor 4 at overcoat 14.In addition, in this case,, can reduce weight, simultaneously except casting, can also make overcoat 14 with the method for punching press etc. because the shape of shell 14 is simplified.For this reason, also can reduce the manufacture cost of compressor 4.
In addition, in this compressor 4, with bolt 56 precessions be formed on than diameter cylinder part 16 thicker regional 26 in axial bore 28 in, by bolt 56, cylinder head 52 is fixed in than diameter cylinder part 16.Therefore, cylinder head 52 and higher than the sealing between the diameter cylinder part 16, thus can prevent high pressure CO
2Refrigeration agent is from cylinder head 52 with than spilling the gap between the diameter cylinder part 16.
The present invention is not restricted to the described embodiments, and can carry out multiple modification.In one embodiment, cylinder seat 22 and be unit disconnected from each other than diameter cylinder part 16 has the cylinder seat that strikes up partnership and than the overcoat of diameter cylinder part but also can use.Under the sort of situation, for leaning device 38 grades are contained in the crank chamber 24, overcoat is formed on separably than between diameter cylinder part and the inclined cylinder part.In addition, cylinder seat 22 and be unit disconnected from each other than diameter cylinder part 16 just can use the cylinder seat of being made by alumina-base material, but cylinder seat is made by the high strength iron preferably.
In addition, in one embodiment, be provided with inclined cylinder part 20 between 18 dividing with the external diameter that reduces gradually than diameter cylinder part 16 with than the minor diameter cylinder part, but than the minor diameter cylinder part divide also can by an end plate with partly be communicated with than diameter cylinder.
In addition, shown in the double dot dash line among Fig. 1, housing 78 can be integrally formed with a plurality of radiating fin 88.Under this situation, for the housing of making by alumina-base material 78, can easily form radiating fin 88, and have higher mechanical precision with complicated shape.In addition, because the radiating fin 88 made by alumina-base material has thermal conductivity preferably, utilize these radiating fin 88 can discharge heat in the compressor 4 fast.Therefore but the heat in the limit compression machine 4 rises, and can further improve its serviceability.
In addition, in the compressor 4 in one embodiment, specifically do not limit housing 78 is fixed to method on the overcoat 14, but the mould that preferably adopts its inside to be equipped with overcoat 14 comes cast housing 78 (aluminium die casting), thereby in die casting, it is fixed on the overcoat 14.In this case, compare with the situation that will be the respectively independent housing of making 78 is fixed on the outer surface of overcoat 14, the operation that housing 78 is fixed on the overcoat 14 will become simpler.Simultaneously, the tight contact performance between housing 78 and the overcoat 14 will be higher, thereby the intensity of shell 12 will be higher also.In addition, high closely contact performance has improved the thermal conductivity between housing 78 and the shell 14, thereby has improved the heat dissipating capacity of radiating fin 88.
In addition, if between housing 78 and overcoat 14, further form the sprayfused coating of making by alumina-base material 89 as illustrated in fig. 2, then the tight contact performance between housing 78 and the overcoat 14 can become higher by sprayfused coating 89, thereby further improve the intensity of shell 12, and the heat dissipation characteristics of radiating fin 88 can be further enhanced also.
In addition, in one embodiment since overcoat 14 divide 18 outer surface not have covering shell 78 than the minor diameter cylinder part, therefore can be formed for antirust coating dividing than the minor diameter cylinder part on 18 the outer surface.But, for dividing 18 than the minor diameter cylinder part, be combined with bearing 71 from the outside, this makes the inducement of getting rusty such as water etc. be difficult to contact, thereby can not necessarily will form this coating.On the other hand, as shown in Figure 3, than can being coated with antirust coating 90 on the thickness portion 26, and cover for example at external peripheral surface than thickness portion 26 than diameter cylinder part 16 without housing 78.That is to say that housing 78 does not need to cover the whole area than the external peripheral surface of diameter cylinder part 16 and inclined cylinder part 20.
At last, fluid machinery of the present invention is not only applicable to the oblique tray type compressor of fixed displacement, and is applicable to swing type and screw compressor.
For the invention of such description, obviously can also many modes change.These variations are not considered to exceed spirit of the present invention and scope, and all these tangible modifications for the person skilled in the art all should be included in the scope of claims.
Claims (7)
1. a fluid machinery comprises a shell, and described shell accommodates: a compression unit, and this compression unit is used for compression working fluid; And a driver element, this driver element is used for sending the power from a running shaft to this compression unit; Described fluid machinery is characterised in that:
Described shell comprises: an overcoat, and this overcoat is made by iron, and is used for described compression unit and driver element are surrounded; And a housing, this housing only is formed on the external peripheral surface of overcoat and by alumina-base material and makes.
2. fluid machinery as claimed in claim 1 is characterized in that,
Described compression unit comprises a cylinder seat and a piston, and this piston is inserted in the cylinder barrel of cylinder seat;
Described driver element comprises: a swash plate, and this swash plate can rotate with described running shaft one; And a pair of guide plate, this is provided with piston guide plate, rotatablely moving of swash plate converted to the to-and-fro motion of piston; And
Described shell comprises a cylinder head, and this cylinder head is connected with overcoat and is made by alumina-base material, is used for supplying working fluid and working fluid is charged into compression unit.
3. fluid machinery as claimed in claim 1 or 2 is characterized in that,
This housing has a mounting portion that is used to install described fluid machinery.
4. fluid machinery as claimed in claim 3 is characterized in that,
This housing also has a radiating fin.
5. fluid machinery as claimed in claim 3 is characterized in that,
This housing is that nationality is by a die casting that accommodates this overcoat.
6. fluid machinery as claimed in claim 5 is characterized in that,
Described shell also comprises a sprayfused coating that is arranged between housing and the overcoat, and this sprayfused coating is made by alumina-base material.
7. fluid machinery as claimed in claim 3 is characterized in that,
Described shell also comprises a coating, and this coating is formed on described beyond the region of objective existence cover and does not have on the zone on the external peripheral surface of covering shell.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005016830 | 2005-01-25 | ||
| JP2005016830A JP2006207391A (en) | 2005-01-25 | 2005-01-25 | Fluid machine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1811182A CN1811182A (en) | 2006-08-02 |
| CN100439708C true CN100439708C (en) | 2008-12-03 |
Family
ID=36650798
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006100043375A Expired - Fee Related CN100439708C (en) | 2005-01-25 | 2006-01-25 | Fluidmaschine |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2006207391A (en) |
| CN (1) | CN100439708C (en) |
| DE (1) | DE102006003370B4 (en) |
| FR (1) | FR2881186A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5018450B2 (en) * | 2007-12-18 | 2012-09-05 | 株式会社豊田自動織機 | Electric compressor |
| CN104695690B (en) * | 2015-03-03 | 2018-04-17 | 佛山意瑞达建筑机械有限公司 | Inclined disc type suction mortar spraying mechanical float |
| CN105626506A (en) * | 2016-02-20 | 2016-06-01 | 杭州佳巨机械配件有限公司 | Connector of plunger pump |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1218875A (en) * | 1997-09-17 | 1999-06-09 | 株式会社丰田自动织机制作所 | Changeable capacity rotary inclined disc type refrigerating compressor |
| CN1220344A (en) * | 1997-11-27 | 1999-06-23 | 株式会社丰田自动织机制作所 | Variable displacement type compressor |
| CN1290813A (en) * | 1999-10-04 | 2001-04-11 | 株式会社丰田自动织机制作所 | Piston type compressor |
| JP2003021066A (en) * | 2001-07-10 | 2003-01-24 | Toyota Industries Corp | Compressor |
| US20030156951A1 (en) * | 2002-02-15 | 2003-08-21 | Hirokazu Kamiya | Compressor |
| JP2004218585A (en) * | 2003-01-16 | 2004-08-05 | Toyota Industries Corp | Compressor and method of manufacturing compressor housing |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08284837A (en) * | 1995-04-07 | 1996-10-29 | Toyota Autom Loom Works Ltd | Cooling structure in clutchless compressor |
| JPH08296553A (en) * | 1995-04-28 | 1996-11-12 | Calsonic Corp | Cam plate type compressor |
| JPH08326929A (en) * | 1995-06-01 | 1996-12-10 | Tomoe Gijutsu Kenkyusho:Kk | Dew drop preventing butterfly valve and manufacture thereof |
| US6706415B2 (en) * | 2000-12-28 | 2004-03-16 | Copeland Corporation | Marine coating |
| JP2003201962A (en) * | 2001-12-28 | 2003-07-18 | Sanden Corp | Electric compressor |
| DE10255680B4 (en) * | 2002-11-28 | 2008-07-31 | Valeo Compressor Europe Gmbh | Axial piston compressors, in particular CO 2 compressors for vehicle air conditioning systems with split cylinder head |
-
2005
- 2005-01-25 JP JP2005016830A patent/JP2006207391A/en active Pending
-
2006
- 2006-01-24 FR FR0600620A patent/FR2881186A1/en not_active Withdrawn
- 2006-01-24 DE DE200610003370 patent/DE102006003370B4/en not_active Expired - Fee Related
- 2006-01-25 CN CNB2006100043375A patent/CN100439708C/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1218875A (en) * | 1997-09-17 | 1999-06-09 | 株式会社丰田自动织机制作所 | Changeable capacity rotary inclined disc type refrigerating compressor |
| CN1220344A (en) * | 1997-11-27 | 1999-06-23 | 株式会社丰田自动织机制作所 | Variable displacement type compressor |
| CN1290813A (en) * | 1999-10-04 | 2001-04-11 | 株式会社丰田自动织机制作所 | Piston type compressor |
| JP2003021066A (en) * | 2001-07-10 | 2003-01-24 | Toyota Industries Corp | Compressor |
| US20030156951A1 (en) * | 2002-02-15 | 2003-08-21 | Hirokazu Kamiya | Compressor |
| JP2004218585A (en) * | 2003-01-16 | 2004-08-05 | Toyota Industries Corp | Compressor and method of manufacturing compressor housing |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1811182A (en) | 2006-08-02 |
| DE102006003370B4 (en) | 2008-01-31 |
| DE102006003370A1 (en) | 2006-07-27 |
| JP2006207391A (en) | 2006-08-10 |
| FR2881186A1 (en) | 2006-07-28 |
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