CN100376800C - Fluid compressor - Google Patents
Fluid compressor Download PDFInfo
- Publication number
- CN100376800C CN100376800C CNB2004100905005A CN200410090500A CN100376800C CN 100376800 C CN100376800 C CN 100376800C CN B2004100905005 A CNB2004100905005 A CN B2004100905005A CN 200410090500 A CN200410090500 A CN 200410090500A CN 100376800 C CN100376800 C CN 100376800C
- Authority
- CN
- China
- Prior art keywords
- pump
- running shaft
- oil circuit
- pump parts
- parts
- 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
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 27
- 230000006835 compression Effects 0.000 claims abstract description 43
- 238000007906 compression Methods 0.000 claims abstract description 43
- 239000000446 fuel Substances 0.000 claims description 27
- 230000008093 supporting effect Effects 0.000 claims description 19
- 230000007246 mechanism Effects 0.000 abstract description 11
- 238000005096 rolling process Methods 0.000 description 16
- 230000000694 effects Effects 0.000 description 8
- 239000000178 monomer Substances 0.000 description 8
- 238000003825 pressing Methods 0.000 description 7
- 230000008878 coupling Effects 0.000 description 6
- 238000010168 coupling process Methods 0.000 description 6
- 238000005859 coupling reaction Methods 0.000 description 6
- 230000015572 biosynthetic process Effects 0.000 description 5
- 230000009471 action Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 239000003507 refrigerant Substances 0.000 description 2
- 229910001018 Cast iron Inorganic materials 0.000 description 1
- 239000004411 aluminium Substances 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000002153 concerted effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000630 rising effect Effects 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- 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
- F04B39/02—Lubrication
-
- 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
- F04B39/02—Lubrication
- F04B39/0223—Lubrication characterised by the compressor type
- F04B39/023—Hermetic compressors
- F04B39/0238—Hermetic compressors with oil distribution channels
- F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
- F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
- F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
- F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/025—Lubrication; Lubricant separation using a lubricant pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/02—Lubrication; Lubricant separation
- F04C29/023—Lubricant distribution through a hollow driving shaft
Abstract
A fluid compressor comprises a rotation shaft having a compression mechanism and an oil passage, a motor, bearings, and a centrifugal pump part for supplying oil through the oil passage. The rotation shaft integrally comprises a main shaft portion, a crank pin eccentrically provided to the main shaft portion, and a sub-bearing supported portion having a smaller diameter than the main shaft portion. The oil passage has a first oil passage extending from a lower end of the sub-bearing supported portion to a lower portion of the main shaft portion, and a second oil passage that is communicated with the first oil passage and extends to an upper end of the crank pin. The second oil passage with a passage portion placed at an outer of that has a smaller diameter than the first oil passage, a plurality of the second oil passages are provided within a plain of said crank pin.
Description
Technical field
The present invention relates to comprise the fluid compression engine of running shaft, relate in particular to a kind of coolant compressor, air or other fluid compression engines of freezing, idle call with oil circuit.
Background technique
Traditional fluid compression engine is opened shown in the 2001-349291 communique as the spy.The spy drives the screw compressor on Fig. 1 of 2001-349291 communique, has in its seal container: the compression mechanical part of compressed fluid, with this compression mechanical part link and have oil circuit running shaft, drive the motor of this running shaft, above above-mentioned motor supporting rotating shaft main bearing, at the supplementary bearing of motor supported underneath running shaft and will be stored in the oil of seal container bottom, by the volume type pump portion of oil circuit to compression mechanical part and bearing fuel feeding.
And, running shaft, its integral body has: be fixed in main shaft part, off-centre on the motor rotor and be located at this main shaft part upper end and the crank portion that is connected with compression mechanical part and be arranged on the main shaft part lower end and the supplementary bearing supporting portion of the minor diameter that supported by supplementary bearing.And, why with the supplementary bearing supporting portion minor diameterization of running shaft, be because can support the cause of supplementary bearing supporting portion more accurately with supplementary bearing.And, can be with the hole of minor diameter form oil circuit with the concentric running shaft of running shaft to the upper end of crank portion from the lower end of supplementary bearing supporting portion.
As traditional fluid compression engine, for example the spy drives the screw compressor shown in the flat 2-245492 communique.Screw compressor shown in the 1st figure of Te Kaiping 2-245492 communique～the 3rd figure has in its seal container: the compression mechanical part of compressed fluid, link with this compression mechanical part and upper spindle with the running shaft of oil circuit, the motor that drives this running shaft, supporting rotating shaft hold portion and will be stored in the oil of seal container bottom, by the centrifugal pump portion (shaft-cup) of oil circuit to compression mechanical part and bearing fuel feeding.
And, running shaft, its integral body has: be fixed in the main shaft part on the motor rotor, the upper end portion that off-centre is located at this main shaft part and the crank portion that is connected with compression mechanical part, with diameter the part that is located at the main shaft part underpart and protrudes downwards from motor.In addition, the oil circuit of running shaft is the structure that has from the lower end the 1st oil circuit that extends to top, is connected and extends to minor diameter the 2nd oil circuit of crank pin upper end in the plane of the 1st oil circuit.
Generally, on fluid compression engine,, wish that the oil circuit by main shaft part is a minor diameter in order to ensure the intensity of running shaft main shaft part.
Open the scroll compressor shown in the 2001-349291 communique as the spy, when the oil circuit of running shaft is formed with minor diameter and running shaft with one heart when lower end, supplementary bearing supporting portion extends to the upper end of crank portion, can not expects to utilize this oil circuit and oil is produced centrifugal force.Therefore, open in the 2001-349291 communique, use volume shape oil pump to guarantee fuel delivery the spy.But, the problem of ultra-high price of the general ratio centrifugal pump of the price portion of volume shape pump portion is arranged.
Screw compressor shown in the Te Kaiping 2-245492 communique, owing to use centrifugal pump portion, thus be cheap structure, but the 2nd oil circuit is connected in the plane of the 1st oil circuit, and have only one the 2nd oil circuit, therefore have the problem of guaranteeing abundant fuel feeding.In addition, because when the oil temperature rose, oil viscosity descended, so reduced the centrifugal effect that acts on inwall and had the problem that to guarantee necessary fuel delivery in centrifugal pump portion.
Summary of the invention
The object of the present invention is to provide a kind of structure can fully guarantee fuel delivery, the fluid compression engine that reliability is superior with cheapness.
For achieving the above object, the present invention is a kind of fluid compression engine, has in its seal container: the compression mechanical part of compressed fluid, with this compression mechanical part link and have oil circuit running shaft, drive the motor of this running shaft, above described motor, support the main bearing of described running shaft, at the supplementary bearing of the described running shaft of supported underneath of described motor and the oil that will be stored in described seal container bottom by the centrifugal pump portion of described oil circuit to described compression mechanical part and described main bearing and supplementary bearing fuel feeding; Described running shaft, its integral body has: be fixed in the main shaft part on the described motor rotor, the upper end portion that off-centre is located at this main shaft part and the crank pin that is connected with described compression mechanical part and the underpart that is located at described main shaft part and the supplementary bearing supporting portion of the minor diameter that supported by described supplementary bearing; The oil circuit of described running shaft has the 1st oil circuit that extends to the bottom of described main shaft part from the lower end of described supplementary bearing supporting portion, and is communicated with the 1st oil circuit and extends to the 2nd oil circuit on the described crank pin; Described the 2nd oil circuit has than the little diameter of described the 1st oil circuit and is positioned at the passage portion of foreign side, and is formed with a plurality of in the planar range of described crank pin.
According to fluid compression engine of the present invention, can fully guarantee fuel delivery with the structure of cheapness, and have superior reliability.
Other purposes of the present invention, feature and advantage can be illustrated according to the following embodiment of the invention of reference accompanying drawing.
Description of drawings
Fig. 1 is the sectional arrangement drawing of the present invention the 1st embodiment's scroll compressor.
Fig. 2 A is the running shaft bottom of Fig. 1 scroll compressor and the sectional arrangement drawing of pump portion, and Fig. 2 B is the IIB-IIB sectional drawing of Fig. 2 A.
Fig. 3 A is the plan view of the present invention the 2nd embodiment's the used pump parts of scroll compressor, Fig. 3 B is the plan view of the present invention the 2nd embodiment's the used pump parts of scroll compressor, and Fig. 3 C is the side view of the present invention the 2nd embodiment's the used pump parts of scroll compressor.
Fig. 4 is the characteristic of fuel delivery plotted curve of the 2nd embodiment's pump parts.
Fig. 5 A is the plan view of the present invention the 3rd embodiment's the used pump parts of scroll compressor, Fig. 5 B is the plan view of the present invention the 3rd embodiment's the used pump parts of scroll compressor, and Fig. 5 C is the side view of the present invention the 3rd embodiment's the used pump parts of scroll compressor.
Fig. 6 A is the pump portion sectional arrangement drawing of the present invention's the 4th embodiment's scroll compressor, and Fig. 6 B is the side view of the pump blade monomer of the present invention's the 4th embodiment's scroll compressor, and Fig. 6 C is the VIC-VIC sectional drawing of Fig. 6 A.
Fig. 7 A is the pump portion sectional arrangement drawing of the present invention's the 5th embodiment's scroll compressor, and Fig. 7 B is the side view of the pump blade monomer of the present invention's the 5th embodiment's scroll compressor, and Fig. 7 C is the VIIC-VIIC sectional drawing of Fig. 7 A.
Fig. 8 A is the pump portion sectional arrangement drawing of the present invention's the 6th embodiment's scroll compressor, and Fig. 8 B is the side view of the pump blade monomer of the present invention's the 6th embodiment's scroll compressor, and Fig. 8 C is the VIIIC-VIIIC sectional drawing of Fig. 8 A.
Fig. 9 A is the pump portion sectional arrangement drawing of the present invention's the 7th embodiment's scroll compressor, and Fig. 9 B is the side view of the pump blade monomer of the present invention's the 7th embodiment's scroll compressor, and Fig. 9 C is the IXC-IXC sectional drawing of Fig. 9 A.
Figure 10 A is the running shaft bottom sectional arrangement drawing of the present invention's the 8th embodiment's scroll compressor, and Figure 10 B is the XB-XB sectional drawing of Figure 10 A.
Figure 11 A is the running shaft bottom sectional arrangement drawing of the present invention's the 9th embodiment's scroll compressor, and Figure 11 B is the XIB-XIB sectional drawing of Figure 11 A.
Embodiment
Below, with reference to description of drawings a plurality of embodiments of the present invention.Same-sign on each embodiment's the accompanying drawing is represented same object or is equivalent to the parts of this object.
With reference to Fig. 1, Fig. 2 A and Fig. 2 B, the present invention the 1st embodiment's scroll compressor is described.Fig. 1 is the sectional arrangement drawing of the present invention the 1st embodiment's scroll compressor, and Fig. 2 A is the running shaft bottom of scroll compressor of Fig. 1 and the sectional arrangement drawing of pump portion, and Fig. 2 B is the IIB-IIB sectional drawing of Fig. 2 A.
Compression mechanical part 2 is that fundamental constitutes with fixed eddy plate 100, rotation whirlpool dish 200 and frame 400.Frame 400 is fixed on the seal container 700, and constitutes the parts that dispose rolling bearing 401.Fixed eddy plate 100, it is that the basic structure part constitutes with platen 101, vortex shape vortex ring 102, suction port 103 and exhaust port 104, and is fixed on the frame 400 by bolt 405.Vortex ring 102 vertically vertically is provided with platen 101 1 sides.Rotation whirlpool dish 200 is that the basic structure part constitutes with platen 201, vortex shape vortex ring 202, propeller boss 203 and back pressure hole.Vortex ring 202 vertically vertically is provided with platen 201 1 sides.Propeller boss 203 vertically is formed at the opposite side (vortex ring opposition side) of platen 201 projectedly.Rotation whirlpool dish 200 is that the foundry goods that will be material is processed into each component part and forms with cast iron or aluminium etc.
Make fixed eddy plate 100 coil 200 Nogami and close the pressing chamber 130 that is constituted, utilize rotatablely moving of rotation whirlpool dish 200 to reduce the compressed action of its volume with the rotation whirlpool.In this compressed action, along with rotatablely moving of rotation whirlpool dish 200, make action fluid process suction pipe 711 and suction port 103 and suck pressing chamber 130, the working fluid that is inhaled into is discharged in the seal container 700 through the exhaust port 104 of compression stroke from fixed eddy plate 100, discharges from seal container 700 through discharge tube 701 again.Therefore, the space in the seal container 700 is keeping head pressure.
In addition, on the side of seal container 700, be provided with hermetic terminal 702 and terminal cover 703, to power to motor 600.Hermetic terminal 702, its perforation also is located on the seal container 700, between the end coil of stator 601 and frame 400 and in the face of the 407a of maximum outside diameter portion of counterweight 407.
In addition, with the side of the seal container 700 of hermetic terminal 702 opposition sides on, be provided with the discharge tube 701 that connects seal container 700, discharge tube 701 is between the end coil of stator 601 and frame 400 and face the 407a of maximum outside diameter portion of counterweight 407.
The drive portion 3 of rotation rotary driving whirlpool dish 200, the motor 600 that constitutes with stator 601 and rotor 602, running shaft 300, to coil European coupling 500, frame 400, rolling bearing 401,803, the propeller boss 203 that 200 rotations stop the critical piece of mechanism as the rotation whirlpool be the fundamental formation.
Running shaft 300 is structures that integral body has main shaft part 302, crank pin 301 and supplementary bearing supporting portion 303.Rolling bearing 401,803, the running shaft supporting portion that formation can cooperate with the main shaft part 302 and the supplementary bearing supporting portion 303 of running shaft 300 flexibly rotatably.Propeller boss 203 is formed on the rotation whirlpool dish 200, can be to moving axially, also can cooperate with the crank pin 301 of running shaft 300 rotatably flexibly as rotation being axial.
Rolling bearing 401 is configured in the upside of motor 600, constitutes the rolling bearing (supplementary bearing) 803 of supplementary bearing portion 800 major components, is configured in the downside of motor 600.On the lower bearing bracket 801 that is fixed on the seal container 700, fixing shell 802 by bolt 805.Insert shell 802 from the top with rolling bearing 803, and the side installs outer housing cover 804 more from it.
The centrifugal effect of utilization in the pump portion 900 of running shaft 300 rotation holds from the pump subordinate to suck the oil that is stored in the seal container 700 bottom oil grooves 730, and 311 fuel feeding of the oil circuit in being formed at running shaft 300.
The oil circuit 311 of running shaft 300 is to have the 1st oil circuit 311a that extends to main shaft part 302 bottoms from the lower end of supplementary bearing supporting portion 303, and be communicated with and extend to the structure of the 2nd oil circuit 311b of crank pin 301 upper ends with the 1st oil circuit 311a.The 1st oil circuit 311a is coaxial with running shaft 300.The 2nd oil circuit 311b, its diameter are littler and have the passage portion of position foreign side than the 1st oil circuit 311a, and have formed a plurality of (being two in the present embodiment) in the planar range of crank pin 301.The circumferential edge portions of the 2nd oil circuit 311b and the 1st oil circuit 311a intersects to form, and can be communicated with more longways vertically.And the 2nd oil circuit 311b is configured in the position with running shaft 300 center off-centre, and this off-centre can play the effect of the 2nd centrifugal pump.
Compression mechanical part 2, when the rotation of crank pin 301 by the running shaft 300 that links with motor 600 produces eccentric rotation, rotation whirlpool dish 200, it can not rotation be rotated motion with respect to fixed eddy plate 100 because of the anti-locking mechanism of rotation of European coupling 500, makes gas pass through suction pipe 711 and suction port 103 sucks in the pressing chamber 130 that is formed by vortex shape vortex ring 102 and 202.Utilize rotatablely moving of rotation whirlpool dish 200, pressing chamber 130 moves to central part on one side and reduces volume and gas is compressed on one side, by exhaust port 104 pressurized gas is discharged to the discharge chamber.Be discharged to the gas of discharging the chamber, be circulated in compression mechanical part 3 and motor 600 around after, discharge outside compressor from discharge tube 701.
In addition, on the platen 201 of rotation whirlpool dish 200, be provided with the back pressure hole that pressing chamber 130 is communicated with the back pressure chamber 411 that rotates the back side, remain on pressure (intermediate pressure) between suction pressure and the head pressure with pressure with back pressure chamber 411.Being formed at the rotation whirlpool and coiling the back pressure chamber 411 of 200 back side, is to center on and the space of formation with rotation whirlpool dish 200, frame 400 and fixed eddy plate 100.Therefore, frame 400 also double as form the parts of back pressure chamber 411.
Be arranged on the seal ring 410 on the groove 409 of frame 400, can prevent to discharge gas and flow into back pressure chamber 411.Rotation whirlpool dish 200, by the intermediate pressure of back pressure chamber 411 and act on seal ring 410 inboards head pressure make a concerted effort be pressed on the fixed eddy plate 100.
At this moment, the internal diameter of seal ring 410 is littler than the external diameter of rolling bearing 401.Owing to can adopt such structure, so in the present embodiment, rolling bearing 401 can be inserted frame 400 from the rotary drive mechanism side of frame 400, and can be with housing cap 403 that the rolling bearing 401 that is inserted is fixing.On housing cap 403, be provided with sliding bearing 402.Housing cap 403 is formed separately with frame 400.Housing cap 403 is fixed on the frame 400 by bolt 406.Why using bolt like this, is because therefore the cause in sealed frame lid 403 and the gap of frame 400 reliably, can suppress the leakage of oil from the fuel feeding path.In addition, housing cap 403 is by the part of inserting the inboard and pushing rolling bearing 401 of frame 400, and and be abutted against the rotary drive mechanism side end face of frame 400 and the part that is fixed on it constitutes.
Like this, counterweight cover 404 has sealed the space between the end coil end face of frame 400 and stator 601.That is, in fact the outer side space of counterweight 407 407a of maximum outside diameter portion is balanced counterweight cover 404 sealings.
Below, the fuel feeding path is described.When running shaft 300 rotation, utilize pump portion 900 that the oil in the oil groove 730 are sent to oil circuit 311 in the running shaft.Be sent to the part of the oil in the oil circuit 311, flow to supplementary bearing 803, return oil groove 730 then as rolling bearing by cross-drilled hole 312.Arrive the oil on crank pin 301 tops by oil circuit 311,, flow to rolling bearing 401 again by swivel bearing 210.Lubricated the oil of rolling bearing 401, nearly all returned oil groove 730 by oil exit pipe 408.Lubricated the part of the oil of rolling bearing 401, arrive counterweight 407 by the gap between housing cap 403 and the running shaft 300, and splash by counterweight 407, but can be attached on the inner face of sidewall 404b of counterweight cover 404 and be recovered, flow down and return oil groove 730 to motor 600.
In addition, on the end face of the propeller boss 203 that rotates whirlpool dish 200, be provided with fuel feeding oil pocket 205, by rotatablely moving of rotation whirlpool dish 200, fuel feeding oil pocket 205 is reciprocal in the outside and the inboard of seal ring 410, and the part of the oil between swivel bearing 201 and the rolling bearing 401 is transported to back pressure chamber 411.The oil that is transported is after to European coupling 500 fuel feeding, to the runner plate face 105 of fixed eddy plate and the slip surface fuel feeding of the platen 201 of rotation whirlpool dish 200.
Be transported to the oil of back pressure chamber 411, by back pressure hole, or the micro-gap by the runner plate slip surface flows into pressing chamber 130.The oil that flows into pressing chamber 130 is discharged from exhaust port 104 with compressed refrigerant, and separates with refrigerant gas in seal container 700 and return oil groove 730.
According to present embodiment, because running shaft 300 integral body have main shaft part 302 on the rotor 602 that is fixed on motor 600, eccentricly be located at the upper end portion of this main shaft part 302 and the crank pin 301 that links with compression mechanical part 2, be arranged on main shaft part 302 underparts and the supplementary bearing supporting portion 303 of the minor diameter that supported by supplementary bearing 803, so can guarantee running shaft 300 necessary strength, and can support supplementary bearing supporting portion 303 accurately with supplementary bearing 803.
In addition, according to present embodiment, owing to be centrifugal pump portion, can reduce price so compare with positive displacement pump portion.And, because pump blade 902 extends to the underpart of pump parts 901, so, can provide the pump mechanism of high reliability even the effect of the less centrifugal blade 902 that also can be by being configured to pump parts 901 lower ends of the oil mass of oil groove 730 is given full play to supply capability.
And, according to present embodiment, because the oil circuit 311 of running shaft 300, be to have the 1st oil circuit 311a that extends to main shaft part 302 bottoms from the lower end of supplementary bearing supporting portion 303, reach the structure that is communicated with and extends to the 2nd oil circuit 311b of crank pin 301 upper ends with the 1st oil circuit 311a, the 2nd oil circuit 311b, its diameter is littler and have a passage portion that is positioned at foreign side than the 1st oil circuit 311a, and in the planar range of crank pin 301, formed a plurality of, so can satisfy above-mentioned running shaft 300 structures, can in the limited sectional area of running shaft 300, guarantee big centrifugal force and big flow path cross sectional area again.Therefore, the 2nd oil circuit 311b has the function as the 2nd centrifugal pump, can fully guarantee fuel delivery with the structure of cheapness, and can become the superior scroll compressor of reliability.
Below, with reference to Fig. 3 A～Figure 11 B the 2nd～the 9th embodiment of the present invention is described.These the 2nd～the 9th embodiments have the structure different with the 1st embodiment as described below, and other each points and the 1st embodiment are basic identical.
With reference to Fig. 3 A～Fig. 4 the 2nd embodiment is described.Fig. 3 A～3C is the explanatory drawing of the used pump parts of the 2nd embodiment's scroll compressor, and Fig. 3 A is a plan view, and Fig. 3 B is a plan view, and Fig. 3 C is a side view.Fig. 4 is the characteristic of fuel delivery plotted curve of the 2nd embodiment's pump parts.
In the 2nd embodiment, the parts that constitute pump portion 900 are pump parts 901, do not have the 1st embodiment's pump blade 902.Pump parts 901 are basic shape with the cone shape, with the connecting part of running shaft 300 be cylindric, with running shaft 300 opposition sides are flat patterns, and with the slick and sly curve formation connecting part and the flat pattern of opposition side end face.
According to the 2nd embodiment, because centrifugal effect integrally acts on the cross-section in the flat pattern of pump parts 901, thus strengthened being present in the supply capabilities of oil in the pump parts 901, and can not be subjected to the influence of oil viscosity and fuel feeding stably.Promptly, when rising of oil temperature and oil viscosity decline, pump parts 901 with simple cone shape, then can shown in the characteristic (b) of Fig. 4, fuel delivery be reduced sharp, but flat pattern pump parts 901 with the 2nd embodiment, then can shown in the characteristic (a) of Fig. 4, can obtain fuel delivery and change little and stable fuel delivery.
In addition, according to the 2nd embodiment,,, therefore be cheap structure so can constitute pump portion 900 with parts owing to can obtain stable fuel delivery as described above.
Below, with reference to Fig. 5 A～Fig. 5 C the 3rd embodiment is described.Fig. 5 A～Fig. 5 C is the explanatory drawing of the present invention the 3rd embodiment's the used pump parts of scroll compressor, and Fig. 5 A is a plan view, and Fig. 5 B is a plan view, and Fig. 5 C is a side view.
In the 3rd embodiment, pump parts 901 are basic shape with the drum, with the connecting part of running shaft 300 be cylindric, with running shaft 300 opposition sides are flat patterns.According to the 3rd embodiment's pump parts 901, because its basic shape is a drum, so can become more cheap structure.
Below, with reference to Fig. 6 A～Fig. 6 C the 4th embodiment is described.Fig. 6 A～Fig. 6 C is the explanatory drawing of pump portion of the present invention the 4th embodiment's scroll compressor, and Fig. 6 A is a sectional arrangement drawing, and Fig. 6 B is the side view of its pump blade monomer, and Fig. 6 C is the VIC-VIC sectional drawing of Fig. 6 A.
In the 4th embodiment, in pump parts 901, be provided with protruding 901c.Be configured in the pump parts 901 and, be subjected to driven pump parts 901 inner fluid inertial force, and be subjected to and the opposite power of running shaft 300 sense of rotation by running shaft 300 with the pump blade 902 of pump parts 901 rotations.For supporting effect power on pump blade 902, opposite with sense of rotation, in pump parts 901, be provided with protruding 901c, and as the link stopper of pump blade 902.Owing in pump parts 901, be provided with protruding 901c, therefore can support pump blade 902 reliably, and can improve the reliability of pump portion 900 with simple, cheap structure.And, pump blade 902, its lower end extends to till the cylindrical portions may of pump parts 901, and top extends in the oil circuit 311.
Below, with reference to Fig. 7 A～Fig. 7 C the 5th embodiment is described.Fig. 7 A～Fig. 7 C is the pump portion explanatory drawing of the present invention the 5th embodiment's scroll compressor.Fig. 7 A is a pump portion sectional arrangement drawing, and Fig. 7 B is the side view of pump blade monomer, and Fig. 7 C is the VIIC-VIIC sectional drawing of Fig. 7 A.
In the 5th embodiment, in pump parts 901, be provided with a pair of protruding 901c.Be provided with this a pair of protruding 901c at two places that face mutually.Pump blade 902, its both side ends is clamped in respectively between a pair of protruding 901c.Therefore, no matter, can both support pump blade 902 reliably corresponding to just commentaries on classics, the counter-rotating of running shaft 300, and can fuel feeding.
Below, with reference to Fig. 8 A～Fig. 8 C the 6th embodiment is described.Fig. 8 A～Fig. 8 C is the explanatory drawing of pump portion of the present invention the 6th embodiment's scroll compressor, and Fig. 8 A is a pump portion sectional arrangement drawing, and Fig. 8 B is the side view of pump blade monomer, and Fig. 8 C is the VIIIC-VIIIC sectional drawing of Fig. 8 A.
The 6th embodiment, compare with the 5th embodiment, its pump blade 902 extends to the underpart this point difference of pump parts 901, other all identical, according to the 6th embodiment, the same with the 1st embodiment, even tailing off, the oil mass of oil groove 730 also can utilize the effect that is configured to pump parts 901 underpart centrifugal blades 902, give full play to supply capability, so can obtain the pump mechanism of high reliability.
Below, with reference to Fig. 9 A～Fig. 9 C the 7th embodiment is described.Fig. 9 A～Fig. 9 C is the pump portion explanatory drawing of the present invention's the 7th embodiment's scroll compressor.Fig. 9 A is a pump portion sectional arrangement drawing, and Fig. 9 B is the side view of pump blade monomer, and Fig. 9 C is the IXC-IXC sectional drawing of Fig. 9 A.
The 7th embodiment compares with the 6th embodiment, and it is different to be formed the sphere this point in the pump parts 901 and the shape of the connecting part opposition side of running shaft 300, and other are all identical.According to the 7th embodiment, since with respect to cone shape, drum, its pump parts 900 inwalls, bigger with respect to the inclination in running shaft 300 axle center, so strengthened the centrifugal pump effect, the pump mechanism of high reliability can obtain stable supply capability, so can be provided.
Below, with reference to Figure 10 A and Figure 10 B the 8th embodiment is described.Figure 10 A and Figure 10 B are the running shaft bottom explanatory drawings of the present invention the 8th embodiment's scroll compressor.Figure 10 A is a running shaft bottom sectional arrangement drawing, and Figure 10 B is the XB-XB sectional drawing of Figure 10 A.
The 8th embodiment divides formation double-layered cylinder shape with the outer circumference portion of pump parts 901.The outer space of pump parts 901 is towards the lower aperture of supplementary bearing portion 800.The inner space of pump parts 901 is identical with the 1st embodiment.
According to the 8th embodiment, be configured in the cylinder-like part of pump parts 901 circumference, brought into play the 3rd centrifugal pump effect.From the oil that discharge the 3rd centrifugal pump upper end, be used to the lubricated supplementary bearing 803 that is disposed at supplementary bearing portion 800.Therefore, can be stably to supplementary bearing 803 fuel feeding, and because the oil of supplying with to pump parts 901 is the fuel feeding path of other system, so can obtain the oil supply structure of high reliability with simple designs.
Below, with reference to Figure 11 A and Figure 11 B the 9th embodiment is described.Figure 11 A and Figure 11 B are the running shaft bottom explanatory drawings of the present invention the 9th embodiment's scroll compressor.Figure 11 A is a running shaft bottom sectional arrangement drawing, and Figure 11 B is the XIC-XIC sectional drawing of Figure 11 A.
The 9th embodiment forms the pump parts 901 and the combining mechanism of running shaft 300 on the screw thread of the coiling direction with worm tooth identical with the sense of rotation of running shaft 300.Because pump parts 901, accept and the rightabout power of running shaft 300 sense of rotation, so utilize act on pump parts 901, with the rightabout power of running shaft 300 sense of rotation, the screw thread of combining mechanism is subjected to the power towards tightening direction, can not come off and the pump mechanism of high reliability from running shaft 300 so can obtain pump parts 901.
Above-described is for embodiment's record, but the present invention is not limited to this, can carry out various changes and correction in spirit of the present invention and scope of invention.
Claims (9)
1. fluid compression engine, in its seal container, have: the compression mechanical part of compressed fluid, with this compression mechanical part link and have oil circuit running shaft, drive the motor of this running shaft, above described motor, support the main bearing of described running shaft, at the supplementary bearing of the described running shaft of supported underneath of described motor and the oil that will be stored in described seal container bottom by the centrifugal pump portion of described oil circuit to described compression mechanical part and described main bearing and supplementary bearing fuel feeding, it is characterized in that:
Described running shaft, its integral body has: be fixed in the main shaft part on the described motor rotor, the upper end portion that off-centre is located at this main shaft part and the crank pin that is connected with described compression mechanical part, be located at the underpart of described main shaft part and the supplementary bearing supporting portion of the minor diameter that supported by described supplementary bearing
The oil circuit of described running shaft has the 1st oil circuit that extends to the bottom of described main shaft part from the lower end of described supplementary bearing supporting portion, and is communicated with the 1st oil circuit and extends to the 2nd oil circuit on the described crank pin,
Described the 2nd oil circuit has than the little diameter of described the 1st oil circuit and is positioned at the passage portion of foreign side, and is formed with a plurality of in the planar range of described crank pin.
2. fluid compression engine according to claim 1 is characterized in that: described the 1st oil circuit and described rotating shaft coaxle, and the circumferential edge portions of described the 2nd oil circuit and described the 1st oil circuit, intersect to form in the mode that is communicated with more longways vertically.
3. fluid compression engine according to claim 1, it is characterized in that: described pump portion, have the pump parts of the tubular that is installed in described running shaft underpart and be configured in the interior pump blade of these pump parts, described pump parts, by the part that is installed in described running shaft underpart and constituting from the part that this part is extended downwards and flowing path section diminishes, described pump blade has with the described consistent profile of pump components interior shape and is pressed into lower end in described pump parts.
4. fluid compression engine according to claim 3 is characterized in that: the part that the flowing path section of described pump parts diminishes is formed spherical shape.
5. fluid compression engine according to claim 1, it is characterized in that: described pump portion, have the tubular pump parts that are installed in described running shaft underpart and be configured in the interior pump blade of these pump parts, and the pump parts have the projection that stops described pump blade to rotate.
6. fluid compression engine according to claim 1 is characterized in that: form described pump portion, the protruding clamping pump blade of these pump parts by the pump parts of tubular.
7. fluid compression engine according to claim 1, it is characterized in that: described pump portion, pump parts with tubular, the connecting part of these pump parts and described running shaft, the screw thread of the coiling direction by having the worm tooth identical and combination with described running shaft sense of rotation.
8. fluid compression engine according to claim 1 is characterized in that:
Described pump portion is formed by cylindric pump parts, and the connecting part of these pump parts and described running shaft is cylindric, and with the opposition side of this connecting part be flat pattern.
9. fluid compression engine according to claim 1 is characterized in that:
Described pump portion is formed by double-layered cylinder shape pump parts, and the outer space of these pump parts is towards the lower aperture of described supplementary bearing portion.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003379436A JP2005140066A (en) | 2003-11-10 | 2003-11-10 | Fluid compressor |
| JP2003379436 | 2003-11-10 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1616828A CN1616828A (en) | 2005-05-18 |
| CN100376800C true CN100376800C (en) | 2008-03-26 |
Family
ID=34689487
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004100905005A Expired - Fee Related CN100376800C (en) | 2003-11-10 | 2004-11-10 | Fluid compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20050180871A1 (en) |
| JP (1) | JP2005140066A (en) |
| KR (1) | KR100657038B1 (en) |
| CN (1) | CN100376800C (en) |
Families Citing this family (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4696153B2 (en) * | 2008-12-15 | 2011-06-08 | 日立アプライアンス株式会社 | Rotary compressor |
| BRPI0902430A2 (en) * | 2009-07-24 | 2011-04-05 | Whirlpool Sa | airtight compressor |
| CN102102671B (en) * | 2009-12-17 | 2012-11-07 | 广东美芝制冷设备有限公司 | Oil supply device of compressor and application thereof |
| KR101400614B1 (en) * | 2010-10-06 | 2014-05-30 | 가부시키가이샤 아루박 | Eccentric rotation drive device |
| CN105190045B (en) * | 2013-06-05 | 2017-04-26 | Lg电子株式会社 | Scroll compressor |
| US9938977B2 (en) * | 2015-02-03 | 2018-04-10 | Emerson Climate Technologies, Inc. | Compressor with oil pump assembly |
| EP3001039B1 (en) * | 2015-09-11 | 2019-06-19 | Pfeiffer Vacuum Gmbh | Vacuum pump |
| AT15828U1 (en) * | 2016-12-27 | 2018-07-15 | Secop Gmbh | LUBRICANT CONSUMPTION FOR A REFRIGERANT COMPRESSOR AND REFRIGERANT COMPRESSOR |
| CN106949060B (en) * | 2017-04-19 | 2019-03-05 | 西安庆安制冷设备股份有限公司 | A kind of rotor-type compressor oil suction structure and its design method |
| TR201712410A2 (en) * | 2017-08-21 | 2019-03-21 | Arcelik As | A COMPRESSOR WITH INCREASED LUBRICATION PERFORMANCE |
| KR102422698B1 (en) * | 2020-11-06 | 2022-07-20 | 엘지전자 주식회사 | Hermetic compressor |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02245492A (en) * | 1989-08-28 | 1990-10-01 | Hitachi Ltd | Scroll compressor |
| CN1176350A (en) * | 1996-09-06 | 1998-03-18 | 三菱重工业株式会社 | Scroll-type compressor |
| US6196817B1 (en) * | 1998-12-15 | 2001-03-06 | Denso Corporation | Compresser with lubricating oil control |
| JP2001349291A (en) * | 2000-06-08 | 2001-12-21 | Hitachi Ltd | Scroll compressor |
| US6484846B1 (en) * | 2000-10-25 | 2002-11-26 | White Consolidated Industries, Inc. | Compressor oil pick-up tube |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2743673A (en) * | 1950-08-01 | 1956-05-01 | American Crucible Products Com | Pump-motor unit |
| US2766027A (en) * | 1953-10-21 | 1956-10-09 | Paul A Herr | Apparatus for controlling humidity conditions in air |
| US4140441A (en) * | 1977-04-11 | 1979-02-20 | Patterson Williams G | Turbomolecular pump lubrication system |
| US4488855A (en) * | 1982-12-27 | 1984-12-18 | The Trane Company | Main bearing lubrication system for scroll machine |
| JPS60206989A (en) * | 1984-03-30 | 1985-10-18 | Mitsubishi Electric Corp | Scroll type fluid machine |
| KR870002381A (en) * | 1985-08-23 | 1987-03-31 | 미다 가쓰시게 | Shroul Compressor |
| JPH0647991B2 (en) * | 1986-05-15 | 1994-06-22 | 三菱電機株式会社 | Scroll compressor |
| US4850819A (en) * | 1987-11-20 | 1989-07-25 | Copeland Corporation | Motor compressor bearing assembly |
| US5533875A (en) * | 1995-04-07 | 1996-07-09 | American Standard Inc. | Scroll compressor having a frame and open sleeve for controlling gas and lubricant flow |
| US6457561B1 (en) * | 2000-05-25 | 2002-10-01 | Bristol Compressors, Inc. | Viscous pumping system |
| KR100422367B1 (en) * | 2001-07-14 | 2004-03-12 | 삼성광주전자 주식회사 | Oil pickup apparatus for Hermetic compressor |
| AU2002216447A1 (en) * | 2001-12-17 | 2003-06-30 | Lg Electronics Inc. | Crank shaft in dual capacity compressor |
| US6752605B2 (en) * | 2002-10-15 | 2004-06-22 | Tecumseh Products Company | Horizontal two stage rotary compressor with a bearing-driven lubrication structure |
-
2003
- 2003-11-10 JP JP2003379436A patent/JP2005140066A/en active Pending
-
2004
- 2004-11-08 US US10/982,927 patent/US20050180871A1/en not_active Abandoned
- 2004-11-09 KR KR1020040090683A patent/KR100657038B1/en active IP Right Grant
- 2004-11-10 CN CNB2004100905005A patent/CN100376800C/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH02245492A (en) * | 1989-08-28 | 1990-10-01 | Hitachi Ltd | Scroll compressor |
| CN1176350A (en) * | 1996-09-06 | 1998-03-18 | 三菱重工业株式会社 | Scroll-type compressor |
| US6196817B1 (en) * | 1998-12-15 | 2001-03-06 | Denso Corporation | Compresser with lubricating oil control |
| JP2001349291A (en) * | 2000-06-08 | 2001-12-21 | Hitachi Ltd | Scroll compressor |
| US6484846B1 (en) * | 2000-10-25 | 2002-11-26 | White Consolidated Industries, Inc. | Compressor oil pick-up tube |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100657038B1 (en) | 2006-12-12 |
| JP2005140066A (en) | 2005-06-02 |
| KR20050045850A (en) | 2005-05-17 |
| US20050180871A1 (en) | 2005-08-18 |
| CN1616828A (en) | 2005-05-18 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR930004198B1 (en) | Scroll compressor | |
| US6746215B2 (en) | Compressor | |
| CN100376800C (en) | Fluid compressor | |
| CN102257278B (en) | Sealed compressor | |
| KR101658711B1 (en) | Scoroll compressor | |
| MXPA01001070A (en) | Oldham coupling for scroll machine. | |
| JP4939884B2 (en) | Fluid compressor | |
| JP4832040B2 (en) | Compressor | |
| JP2007100543A (en) | Scroll compressor | |
| US7179069B2 (en) | Motor compressor lubrication | |
| JP2004316537A (en) | Fluid compressor | |
| JPS61226587A (en) | Scroll type compressor | |
| JPS593182A (en) | Closed-type electric motor-driven compressor | |
| CN101769254A (en) | Rotary compressor | |
| JP2005140064A (en) | Electric compressor | |
| CN110168225A (en) | Compressor | |
| JP4243805B2 (en) | Fluid compressor | |
| KR100341273B1 (en) | structure for supporting pressure sharing plate in scroll-type compressor | |
| JP4433457B2 (en) | Scroll compressor | |
| JPH03124985A (en) | Sealed scroll compressor | |
| JPH0531275Y2 (en) | ||
| KR100865138B1 (en) | Crank-shaft for hermetic compressor | |
| JP2006299837A (en) | Liquid compressor | |
| JPH0754788A (en) | Closed type compressor | |
| JP5520762B2 (en) | Scroll compressor, electric compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee | ||
| CP01 | Change in the name or title of a patent holder |
Address after: Tokyo, Japan Patentee after: Hitachi Appliances, Inc. Address before: Tokyo, Japan Patentee before: Hitachi Appliances, Inc. |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20160901 Address after: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee after: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. Address before: Tokyo, Japan Patentee before: Hitachi Appliances, Inc. |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20180703 Address after: Tokyo, Japan Patentee after: HITACHI-JOHNSON CONTROLS AIR CONDITIONING, Inc. Address before: Hongkong aoteng Plaza No. 8 Chinese Kowloon Linze street 12 floor Patentee before: Johnson Controls Hitachi air conditioning technology (Hong Kong) Co.,Ltd. |
|
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080326 Termination date: 20211110 |