CN106662093A - Open-type compressor - Google Patents

Open-type compressor Download PDF

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Publication number
CN106662093A
CN106662093A CN201580033419.XA CN201580033419A CN106662093A CN 106662093 A CN106662093 A CN 106662093A CN 201580033419 A CN201580033419 A CN 201580033419A CN 106662093 A CN106662093 A CN 106662093A
Authority
CN
China
Prior art keywords
oil supply
supply gallery
drive shaft
oil
radial
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
Application number
CN201580033419.XA
Other languages
Chinese (zh)
Inventor
宫本善彰
木全央幸
后藤利行
佐藤创
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority to JP2014162441A priority Critical patent/JP6462265B2/en
Priority to JP2014-162441 priority
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Priority to PCT/JP2015/072069 priority patent/WO2016021590A1/en
Publication of CN106662093A publication Critical patent/CN106662093A/en
Pending legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00Component 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
    • F04B39/02Lubrication
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04BPOSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08Multi-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
    • F04B27/10Multi-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
    • F04B27/1036Component parts, details, e.g. sealings, lubrication
    • F04B27/109Lubrication
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02Lubrication; Lubricant separation

Abstract

Provided is an open-type compressor with which it is possible to prevent a reduction in oil supply amount caused by an increase in flow-path pressure loss particularly in a high rotational speed range, and to improve reliability in lubrication performance. Disclosed is an open-type compressor (1) comprising: a drive shaft (9) having one end protruding outside a housing (2); an oil supply pump (37) provided in an outer circumferential section of the drive shaft (9); a pump chamber (39) that is formed around the drive shaft (9), and into which oil pumped up by the oil supply pump (37) is discharged; an axial-direction oil supply passage (41) that is pierced inside the drive shaft (9) along the direction of the axis L thereof, and that supplies the oil from the pump chamber (39) to a sliding part; and a radial-direction oil supply passage (40) that guides the oil in the pump chamber (39) to the axial-direction oil supply passage (41). The axial-direction oil supply passage (41) is provided in a position that is decentered by a predetermined dimension [delta]h with respect to the axis L of the drive shaft (9). The radial-direction oil supply passage (40) is provided on a side toward which the axial-direction oil supply passage (41) is decentered.

Description

Open compressor
Technical field
The present invention relates to a kind of can be by by being arranged at the periphery of drive shaft and utilizing the powered fuel feeding of the drive shaft The oil that pump draws, is supplied to the open compressor of sliding position by the oil supply gallery worn vertically in drive shaft.
Background technology
The one end that the drive shaft of enclosure interior is rotatably supported in by bearing is prominent to hull outside, from outer Portion is obtained in the open compressor of power and powered horizontal arrangement type, when using the lubrication that store oil portion is drawn by oil feed pump In the case of oil, and the pressure fuel system that the oil is supplied to sliding positions such as bearings and is lubricated, such as the institute of patent document 1 Show, be configured to be arranged by the powered oil feed pump of the drive shaft in the periphery of drive shaft, and will be drawn by the oil feed pump Oil, is supplied to sliding position by the oil supply gallery worn vertically in drive shaft.
In the case of hermetic type compressor, no matter longitudinal type or horizontal arrangement type, generally using following structure, i.e. driving The shaft end of moving axis arranges the oil feed pump of centrifugal, positive displacement etc., and the lubricating oil being filled in closed container is drawn by oil feed pump, And directly the oil is supplied to sliding position by the oil supply gallery worn vertically in drive shaft.Force to supply for this The compressor of oily mode, Patent Document 2 discloses the oil supply gallery axially inside worn in drive shaft, relative to the axis Offset given size and arrange, and the compressor of oil supply performance is improved using centrifugal force.
Conventional art document
Patent document
Patent document 1:Japanese Unexamined Patent Publication 2005-282446 publications
Patent document 2:Japanese Unexamined Patent Publication 8-219063 publication
The summary of invention
The invention technical task to be solved
As described above, in the compressor for forcing fuel system is employed, in the case of hermetic type, without the need for obtaining outside Power and one end of drive shaft is set to into open end, oil supply gallery can be vertically worn, therefore, it is difficult to being produced by centrifugal force Impact and can be directly proportional to the rotating speed of drive shaft increase oil feed pump rotating speed, centrifugal force.Thus, fuel delivery is increased, can Oil supply performance is improved, therefore without special problem.But, in the case of open compressor, need to obtain external impetus, It is difficult to for one end of drive shaft to be set to open end.Accordingly, it would be desirable to temporarily the oil drawn by oil feed pump is expelled to around driving The pump chamber that axle is formed, and from the pump chamber by being arranged radially in the oil supply gallery of drive shaft to the oil supply gallery for wearing vertically For oil supply.
Therefore, the intake section of the oil supply gallery for radially wearing in structure, it is impossible to avoid generation from being caused by centrifugal force Crushing.With regard to the stream crushing, tend to increase as the rotating speed of drive shaft increases, therefore when having axial direction oil supply gallery to set The characteristic especially reduced in high speed area fuel delivery as shown in Figure 3 when being placed on the axis of drive shaft (without acceptance of persons).
The present invention is completed in light of this situation, be its object is to offer one kind and is enabled in particular to suppress high speed area In the reduction of fuel delivery that causes because stream crushing increases, and improve the opening compression of reliability for greasy property Machine.
For solving the means of technical task
1st mode of the present invention is open compressor, and it possesses:Drive shaft, is rotatably supported in housing, its One end is prominent to the hull outside;Oil feed pump, is arranged at the peripheral part of the drive shaft, by the rotation of the drive shaft Driven;Pump chamber, forms around the drive shaft, and discharges the oil drawn by the oil feed pump;Axial oil supply gallery, in institute State and worn along its axis direction in drive shaft, and will supply to sliding position from the oil of the pump chamber;And radial direction oil supply gallery, The drive shaft is arranged at, the oil of the pump chamber is guided to the axial oil supply gallery, it is described in the open compressor Axial oil supply gallery is arranged at the position of the eccentric axis given size relative to the drive shaft, and the radial direction oil supply gallery sets It is placed in the eccentric direction side of the axial oil supply gallery.
1st mode of the invention, the axial oil supply gallery worn in drive shaft, is arranged at relative to drive shaft The position of eccentric axis given size, and the oil of the pump chamber drawn by oil feed pump is guided to the radial direction of axial oil supply gallery Oil supply gallery, is arranged at the eccentric direction of axial oil supply gallery, therefore makes axial oil supply gallery eccentric, and with its eccentric direction Side arranges the passage length that the amount of radial direction oil supply gallery correspondingly shortens radial direction oil supply gallery, can reduce in radial direction oil supply gallery Intake section produce the stream crushing caused by centrifugal force.That is, in not making the eccentric compressor of axial oil supply gallery, radially The passage length of oil supply gallery becomes drive shaft radius, but radial direction oil supply gallery is being arranged at the bias side of axial oil supply gallery To side in the case of, passage length can be shortened compared to drive shaft radius, can corresponding to which reduce stream crushing.And And, by making axial oil supply gallery bias given size, the centrifugation pump efficiency that oil is acted in axial oil supply gallery can be utilized Fruit is improved for the oil supply performance of sliding position.Therefore, the reducing effect by stream crushing in radial direction oil supply gallery be based on The synergy of the raising effect of the oil supply performance of axial oil supply gallery, enables in particular to the drop of the fuel delivery of suppression high speed area It is low, and improve for the reliability of greasy property.
In the open compressor of the 1st mode of the present invention, the radial direction oil supply gallery may be disposed in the bias side To axis upper channel length for shortest length position.
1st mode of the invention, because radial direction oil supply gallery is arranged at the axis upper channel length in eccentric direction For the position of shortest length, the amount therefore, it is possible to the eccentric size with axial oil supply gallery correspondingly shortens radial direction oil supply gallery Passage length, by its length shortest length is set to such that it is able to make that the intake section in radial direction oil supply gallery produces by being centrifuged The stream crushing that power causes is minimized.Thereby, it is possible to improve the fuel delivery of high speed area, and further improve oil supply performance.
In above-mentioned any open compressor of the 1st mode of the present invention, the channel diameter of the axial oil supply gallery The diameter bigger than the channel diameter of the radial direction oil supply gallery can be set to.
1st mode of the invention, by the channel diameter of axial oil supply gallery passage of the specific diameter to oil supply gallery is set to The big diameter of diameter, therefore the centrifugal pump effect caused by bias is readily obtained, and the stream crushing in passage can be reduced. Additionally, to radial direction oil supply gallery and the connecting portion of axial oil supply gallery not produce step difference, burr etc. in the way of connect Processing such that it is able to prevent from producing stream crushing with the connecting portion of axial oil supply gallery in radial direction oil supply gallery, can suppress high The reduction of the fuel delivery of rotary speed area simultaneously improves oil supply performance.
Invention effect
According to the present invention, make axial oil supply gallery eccentric, and with the amount of radial direction oil supply gallery is set in its eccentric direction side Correspondingly shorten the passage length of radial direction oil supply gallery, can reduce the intake section of radial direction oil supply gallery produce by being centrifuged The stream crushing that power causes, and by making axial oil supply gallery bias given size, can utilize in axial oil supply gallery The centrifugal pump effect for acting on oil is improved for the oil supply performance of sliding position, therefore by stream crushing in radial direction oil supply gallery Reducing effect and the synergy of the raising effect of the oil supply performance based on axial oil supply gallery, enable in particular to suppress high rotating speed The reduction of the fuel delivery in region, and improve for the reliability of greasy property.
Description of the drawings
Fig. 1 is the longitudinal sectional view of the open compressor of embodiments of the present invention.
Fig. 2 is the sectional view (A) and its right side view (B) of the drive shaft in above-mentioned open compressor.
Fig. 3 is comparable to the sectional view of the a-a in Fig. 2 (A).
Fig. 4 is disposed on the sectional view equivalent to Fig. 3 of the variation of the radial direction oil supply gallery of above-mentioned drive shaft.
Fig. 5 is the curve map for representing the characteristic of fuel delivery in above-mentioned open compressor.
Specific embodiment
Hereinafter, embodiments of the present invention are illustrated referring to figs. 1 to Fig. 5.
Fig. 1 represents the longitudinal sectional view of the open compressor of embodiments of the present invention, and Fig. 2 represents cuing open for its drive shaft View (A) and its right side view (B), Fig. 3 and Fig. 4 represents respectively the sectional view equivalent to the a-a in Fig. 2 (A).
Open compressor 1 possesses in the procapsid 3 for having Bottom Shape and the circle joined integrally of back casing 4 by bolt 5 Tubular shell 2.
The openend side of the side of procapsid 3 in housing 2, is fixedly installed parts of bearings 6, by this by bolt 7 Radial bearing portion 6A of parts of bearings 6 rotatably supports drive shaft 9 with the rolling bearing 8 being arranged in procapsid 3.Drive The one end of axle 9 is through procapsid 3 and protruding to the outside, and the power from external drive sources such as engines is by belt wheel 10 and electricity Magnet clutch 11 is imported into the protruding parts.
For belt wheel 10, rotatably it is supported in by rolling bearing 14 and procapsid 3 is fixedly installed on by bolt 12 Front end face vibrating part 13 periphery, and in the coil group 15 of its assembled inside electromagnetic clutch 11.Also, with belt wheel 10 relative modes, by the rotor assembly 16 of electromagnetic clutch 11 outside of drive shaft 9 is assembled in bolt 17 by boss portion Jag.In addition, the inner circumferential in the vibrating part 13 is provided with the mechanical sealing member of the through-Penetration portion for potting drive shaft 9 18。
Assembled inside in the side of back casing 4 of housing 2 has compression mechanism 19.Here, compression mechanism 19 is set to into possess one To fixed scroll 20 and the scroll compressor mechanism 19 for turning round vortex 21.In scroll compressor mechanism 19, a pair of fixed scrolls are made 20 and revolution be vortexed 21 deviate 180 ° of phase places and engage, two be vortexed 20,21 between be formed with multiple discharge chambes 22, this vortex Formula compression mechanism 19 is well known by themselves.
Fixed scroll 20 is fastened and fixed to parts of bearings 6 by bolt 23, the inner surface of its end plate back side and back casing 4 it Between be formed with discharge chamber 26.In the end plate of the fixed scroll 20, it is provided with and gas compressed is expelled to into discharge chamber 26 The dump valve 25 of interior discharge port 24 and the either on or off discharge port 24.Also, in back casing 4, can open to be expelled to The compressed gas discharged in chamber 26 are connected to the outside discharge 27 discharged with the discharge pipe arrangement for constituting kind of refrigeration cycle.
Revolution vortex 21 is set to following structure:There is boss portion 28 at the end plate back side, relative to the boss portion 28, setting is made Crank-pin 9A in the interior side of drive shaft 9 is linked by driving lining 29 and floating bearing 30, is led to using the rotation of drive shaft 9 Crossing crank-pin 9A carries out revolution driving.Also, turn round be vortexed 21 the end plate back side by being arranged at the thrust bearing of parts of bearings 6 31 are supported, also, by including the cross slip-ring (Oldham ring) being clipped between the end plate back side and parts of bearings 6 Or the well-known rotation of lock ring (Pin ring) etc. prevents mechanism 32 from preventing rotation, is revolved round the sun relative to fixed scroll 20 Revolution driving.
It is set to following structure:Arrange what is be connected with the suction pipe arrangement of kind of refrigeration cycle side in the periphery of the front of back casing 4 Suction inlet 33, by the low-pressure gas being drawn in intake chamber 34 from the suction inlet 33 pressure of scroll compressor mechanism 19 is drawn into It is compressed in contracting room 22.In present embodiment, so-called ladder scroll compressor mechanism 19 is set to, but is not limited to This, in the ladder scroll compressor mechanism 19, setting makes compression mechanism 19 in fixed scroll 20 and the vortex of revolution vortex 21 Change the step difference portion of wrap height on direction, relative to inner circumferential side wrap height outer circumferential side wrap height improved such that it is able to Carry out not only being capable of in the circumferential but also also the three-dimensional compression of compressed gas in the axial direction.
On the other hand, the desired amount of lubricating oil is filled in the inside of procapsid 3, the bottom Kong Inter in procapsid 3 is set to Store oil portion 35, thus focuses on the store oil portion 35 by oil.It is set to make the oil in the store oil portion 35 to be drawn into confession through suction passage 36 The structure of oil pump 37.
Oil feed pump 37 is set to known rotary volume type pump, and the rotary volume type pump is following structure:Running through The periphery position of the drive shaft 9 of the front end face of procapsid 3 forms eccentric part 9B (referring to Fig. 2), relative to eccentric part 9B, will be Formed between the front end face of procapsid 3 and the end face of vibrating part 13 and the rotor 38 of eccentric rotary is chimeric in cylinder body.
The eccentric part 9B and machine for being formed around drive shaft 9 is discharged to from the oil that store oil portion 35 draws by oil feed pump 37 In pump chamber 39 between tool seal 18.The oil of the pump chamber 39 is drawn into by the radial direction oil supply gallery that is arranged in drive shaft 9 40 and axial oil supply gallery 41 be supplied to the slip such as radial bearing portion 6A, driving lining 29, floating bearing 30, thrust bearing 31 Sliding position of position or mechanical sealing member 18 etc..
As shown in Figures 2 and 3, in the inside of drive shaft 9, the axial oil supply gallery 41 arranged along its axis L is arranged at Relative to the position of axis L bias given size (eccentric size) the Δ h of drive shaft 9.Also, in the inclined of axial oil supply gallery 41 Heart direction arranges and guides the oil in pump chamber 39 to the radial direction oil supply gallery 40 of axial oil supply gallery 41.In present embodiment, will Radial direction oil supply gallery 40 is arranged at the position that its passage length h1 on the axis of eccentric direction is shortest length.Thus, with general The passage length h of the compressor that axial oil supply gallery 41 is arranged on the axis L of drive shaft 9 is compared, can be with Δ h (Δ h=h- H1) corresponding amount correspondingly shortens the passage length h1 of radial direction oil supply gallery 40.
But, in the present invention, however it is not limited to which radial direction oil supply gallery 40 is arranged at as described above the axis of eccentric direction On, and its passage length h1 is set to into the compressor of shortest length, it is also possible to as shown in Figure 4 relative to eccentric direction There is axis the side of constant angle to set up radial direction oil supply gallery 40A.According to the structure, it is also possible to by radial direction oil supply gallery The passage length h2 of 40A is set to the passage length of the compressor than being arranged at axial oil supply gallery 41 on the axis L of drive shaft 9 H is short, and passage length h2 in this case becomes h1 < h2 < h.That is, the oil of pump chamber 39 is guided to the footpath of axial oil supply gallery 41 On the axis for being not limited to be arranged at eccentric direction to oil supply gallery, can be by being arranged at the bias side of axial oil supply gallery 41 To side, can make its passage length ratio that the passage length of the compressor of axial oil supply gallery 41 is set on the axis L of drive shaft 9 It is short.
Also, as described above, when arranging axial oil supply gallery 41 and radial direction oil supply gallery 40,40A, by axial oil supply gallery 41 are set to the blind hole that wears along axis L from one end of crank-pin 9A.On the other hand, need to set radial direction oil supply gallery 40,40A It is the hole of the setting orthogonal with radial direction near the leading section of the blind hole, in order to avoid produce become stream pressure in its cross part (connecting portion) Step difference, burr of the main cause of damage etc..Then, it is set to following structure:The channel diameter d1 of axial oil supply gallery 41 is set It is specific diameter to the channel diameter d2 of oil supply gallery 40,40A big diameter (d1 > d2), it is thus easy in axial oil supply gallery 41 To the centrifugal pump effect caused by bias, and reduce the stream crushing in the passage, and can two passages 40,40A with 41 connecting portion carries out connection processing in the way of portion produces step difference, burr etc..
By structure described above, according to present embodiment, following action effect is played.
In above-mentioned open compressor 1, if electromagnetic clutch 11 is set to ON, it is input into from external drive source by belt wheel 10 Power be passed to drive shaft 9, drive shaft 9 carries out rotation driving.Thus, the revolution vortex 21 of scroll compressor mechanism 19 encloses Revolution revolution driving is carried out around fixed scroll 20, the low-pressure gas being drawn in intake chamber 34 from suction inlet 33 is drawn into into pressure In contracting room 22, it is compressed into high pressure and is expelled in discharge chamber 26 from discharge port 24, from outlet 27 kind of refrigeration cycle is expelled to.
During this period, store oil portion 35 is sucked via suction passage 36 by the powered oil feed pump 37 of the rotation of drive shaft 9 Interior lubricating oil, is drawn into pump chamber 39.The oil being drawn in pump chamber 39 is lubricated to the sliding position of mechanical sealing member 18, and And guide to axial oil supply gallery 41 via radial direction oil supply gallery 40,40A, journal bearing is supplied to by axial oil supply gallery 41 The sliding positions such as portion 6A, driving lining 29, floating bearing 30, thrust bearing 31, are lubricated to each sliding position.To have lubricated The oil of each sliding position concentrates on the bottom i.e. store oil portion 35 of housing 2, is recycled.
Here, in present embodiment, axial oil supply gallery 41 is arranged at into the eccentric regulations of axis L relative to drive shaft 9 The position of size Δ h, and radial direction oil supply gallery 40,40A is arranged at into the eccentric direction side of axial oil supply gallery 41, the footpath The oil in pump chamber 39 is guided to the axial oil supply gallery 41 to oil supply gallery 40,40A.Thereby, it is possible to make its passage length h1, The passage length short (h1 < h2 < h) of compressors of the h2 than being arranged at axial oil supply gallery 41 on the axis L of drive shaft 9.
Therefore, the logical of radial direction oil supply gallery 40,40A is correspondingly shortened with the size Δ h for making the bias of axial oil supply gallery 41 Road length h1, h2, can reduce the stream pressure caused by centrifugal force produced in the intake section of radial direction oil supply gallery 40,40A Damage.Also, by making the eccentric given size Δ h of axial oil supply gallery 41, can utilize and be acted in axial oil supply gallery 41 The centrifugal pump effect of oil is improved for the oil supply performance of sliding position.
Fig. 5 is that transverse axis takes the rotating speed (rpm) of drive shaft 9, the longitudinal axis and takes fuel delivery (cm3/ min) and represent employ it is above-mentioned strong The curve map of the characteristic of fuel delivery in the case of fuel system processed.Relative to theoretical value indicated by the solid line, by axial oil supply gallery In the case that 41 are arranged on axis L, the passage length h of radial direction oil supply gallery is elongated, therefore in height as shown in drawing Rotary speed area fuel delivery is reduced relative to theoretical value.Such as present embodiment, relative to axis L eccentric settings axial direction oil supply gallery 41, and in the case of being arranged at radial direction oil supply gallery 40,40A its eccentric direction side and shorten passage length h1, h2, Neng Gouru Draw ▲ as shown in improve high speed area fuel delivery and close theoretical value.
Therefore, according to present embodiment, the reducing effect by stream crushing in radial direction oil supply gallery 40,40A be based on The synergy of the raising effect of the oil supply performance of axial oil supply gallery 41, can suppress the drop of the fuel delivery of high speed area It is low, and improve for the reliability of greasy property.
Especially, radial direction oil supply gallery 40 is arranged at into position of axis upper channel length h1 in eccentric direction for shortest length Put.Therefore, the passage length of radial direction oil supply gallery 40 is correspondingly shortened with the amount of the eccentric size Δ h of axial oil supply gallery 41 H1, and its length h1 is set to into shortest length, can make what the intake section in radial direction oil supply gallery 40 produced to be drawn by centrifugal force The stream crushing for rising is minimized.Thereby, it is possible to improve the fuel delivery of high speed area, and further improve oil supply performance.
Also, it is with regard to radial direction oil supply gallery 40,40A and axial oil supply gallery 41, the passage of axial oil supply gallery 41 is straight Footpath d1 is set to specific diameter to the channel diameter d2 of oil supply gallery 40,40A big diameter (d1 > d2), therefore is readily obtained axial fuel feeding The centrifugal pump effect caused by bias of passage 41, and the stream crushing in its passage can be reduced.And, to radial direction fuel feeding Passage 40,40A and the connecting portion of axial oil supply gallery 41 not produce step difference, burr etc. in the way of carry out connecting processing, energy Enough prevent from producing stream crushing in two passages 40,40A and 41 connecting portion, therefore by its synergy, can suppress high The reduction of the fuel delivery of rotary speed area, and improve oil supply performance.
Especially, the open compressor 1 of present embodiment is being applicable for use with carrying out the high-speed cruising of more than 3600rpm Pressure fuel system opening screw compressor 1 when, it is possible to increase greasy property.
In addition, the present invention is not limited to the invention of above-mentioned embodiment, can suitably be deformed.For example, above-mentioned enforcement In mode, as one of open compressor 1, the example suitable for scroll compressor is illustrated, but certainly The compressor of other forms, such as rotary, ramp type, reciprocating etc. can be equally applicable to.
Also, with regard to oil feed pump 37, in above-mentioned embodiment, also the example to being suitable for revolving volume type pump is carried out Explanation, but this is not limited to, can be set to the oil feed pump of the other forms such as the pump of screw-type.
Symbol description
1- open compressors, 2- housings, 9- drive shafts, 37- oil feed pumps, 39- pump chambers, 40,40A- radial direction oil supply galleries, 41- axial directions oil supply gallery, the axis of L- drive shafts, Δ h- bias sizes, the passage length of h1, h2- radial direction oil supply gallery, d1- The channel diameter of axial oil supply gallery, the channel diameter of d2- radial direction oil supply galleries.

Claims (3)

1. a kind of open compressor, it possesses:
Drive shaft, is rotatably supported in housing, and one end is to the outside prominent of the housing;
Oil feed pump, is arranged at the peripheral part of the drive shaft, is driven by the rotation of the drive shaft;
Pump chamber, forms around the drive shaft, and discharges the oil drawn by the oil feed pump;
Axial oil supply gallery, wears in the drive shaft along its axis direction, and will supply to cunning from the oil of the pump chamber Dynamic position;And
Radial direction oil supply gallery, is arranged at the drive shaft, and the oil of the pump chamber is guided to the axial oil supply gallery,
In the open compressor,
The axial oil supply gallery is arranged at the position of the eccentric axis given size relative to the drive shaft, and the radial direction is supplied Oily passage is arranged at the eccentric direction side of the axial oil supply gallery.
2. open compressor according to claim 1, wherein,
The radial direction oil supply gallery is arranged at position of the axis upper channel length in the eccentric direction for shortest length.
3. open compressor according to claim 1 and 2, wherein,
The channel diameter of the axial oil supply gallery is set to the diameter bigger than the channel diameter of the radial direction oil supply gallery.
CN201580033419.XA 2014-08-08 2015-08-04 Open-type compressor Pending CN106662093A (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2014162441A JP6462265B2 (en) 2014-08-08 2014-08-08 Open type compressor
JP2014-162441 2014-08-08
PCT/JP2015/072069 WO2016021590A1 (en) 2014-08-08 2015-08-04 Open-type compressor

Publications (1)

Publication Number Publication Date
CN106662093A true CN106662093A (en) 2017-05-10

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Application Number Title Priority Date Filing Date
CN201580033419.XA Pending CN106662093A (en) 2014-08-08 2015-08-04 Open-type compressor

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Country Link
EP (1) EP3150855B1 (en)
JP (1) JP6462265B2 (en)
KR (2) KR20180112091A (en)
CN (1) CN106662093A (en)
AU (1) AU2015300143B2 (en)
WO (1) WO2016021590A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5427602A (en) 1994-08-08 1995-06-27 Aluminum Company Of America Removal of suspended particles from molten metal

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05149277A (en) * 1991-11-26 1993-06-15 Mitsubishi Heavy Ind Ltd Horizontal type closed scroll compressor
CN2688935Y (en) * 2004-01-21 2005-03-30 柳州高新区浦发汽车空调有限公司 Volumetric vortex fluid compressor
JP2005282446A (en) * 2004-03-29 2005-10-13 Mitsubishi Heavy Ind Ltd Scroll compressor
JP2012097577A (en) * 2010-10-29 2012-05-24 Daikin Industries Ltd Compressor
CN202520559U (en) * 2012-03-14 2012-11-07 广东美芝精密制造有限公司 Crankshaft structure of rolling rotor compressor

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04279792A (en) * 1991-03-08 1992-10-05 Toshiba Corp Fluid compressor
JPH08219063A (en) 1995-02-13 1996-08-27 Daikin Ind Ltd Lubricating oil feeding structure for rotary shaft

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05149277A (en) * 1991-11-26 1993-06-15 Mitsubishi Heavy Ind Ltd Horizontal type closed scroll compressor
CN2688935Y (en) * 2004-01-21 2005-03-30 柳州高新区浦发汽车空调有限公司 Volumetric vortex fluid compressor
JP2005282446A (en) * 2004-03-29 2005-10-13 Mitsubishi Heavy Ind Ltd Scroll compressor
JP2012097577A (en) * 2010-10-29 2012-05-24 Daikin Industries Ltd Compressor
CN202520559U (en) * 2012-03-14 2012-11-07 广东美芝精密制造有限公司 Crankshaft structure of rolling rotor compressor

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KR20180112091A (en) 2018-10-11
AU2015300143B2 (en) 2018-05-10
EP3150855A1 (en) 2017-04-05
WO2016021590A1 (en) 2016-02-11
KR102096139B1 (en) 2020-04-01
EP3150855B1 (en) 2020-04-22
EP3150855A4 (en) 2017-06-28
KR20170010406A (en) 2017-01-31
AU2015300143A1 (en) 2017-01-19
JP6462265B2 (en) 2019-01-30
JP2016037922A (en) 2016-03-22

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Application publication date: 20170510