CN103154521A - Rotary compressor - Google Patents
Rotary compressor Download PDFInfo
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- CN103154521A CN103154521A CN2011800466082A CN201180046608A CN103154521A CN 103154521 A CN103154521 A CN 103154521A CN 2011800466082 A CN2011800466082 A CN 2011800466082A CN 201180046608 A CN201180046608 A CN 201180046608A CN 103154521 A CN103154521 A CN 103154521A
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- pressing chamber
- oil
- refrigeration agent
- clinch
- scroll
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
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- 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
- F04C29/04—Heating; Cooling; Heat insulation
- F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
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- 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
- F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
- F04C18/0269—Details concerning the involute wraps
- F04C18/0292—Ports or channels located in the wrap
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2210/00—Fluid
- F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
- F04C2210/263—HFO1234YF
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
As a result of using a refrigerant comprising at least a hydrofluoroolefin having carbon double bonds, a low ozone layer depletion factor and a low global warming potential, and providing a first compression chamber feed oil path which feeds refrigerating oil to a compression chamber (15) in which the refrigerant has been sealed, it is possible to limit the effect on the global environment and also to limit increases in the temperature of the refrigerant, which is the source of re-expansion and heating and also feeding of refrigerating oil at a high temperature, in other words it is possible to limit decomposition of the refrigerant.
Description
Technical field
The present invention relates to use contain at least not chloride atom and have that the global warming coefficient is low, the refrigeration agent of HF hydrocarbon (hydrofluoro olefin) that have the two keys of carbon and be assembled into rotary compressor in the refrigerating circulatory device of indoor air conditioner, On-vehicle air conditioner, refrigerated warehouse (refrigerator) and other air bells conditioners etc.
Background technique
The refrigeration agent accelerating transition that uses in refrigerating circulatory device to depletion of the ozone layer coefficient is zero HFC(hydrofluorocarbon: the hydrogen fluorohydrocarbon) class (hereinafter referred to as " HFC class refrigeration agent ").Yet the global warming coefficient of this HFC class refrigeration agent is very high.So, the compressor of the refrigeration agent that positive application depletion of the ozone layer coefficient and global warming coefficient are low.But the refrigeration agent that the global warming coefficient is low is in general stable low.Therefore, when the medium-term and long-term use of refrigerating circulatory device at indoor air conditioner, On-vehicle air conditioner, refrigerated warehouse (refrigerator) and other air bells conditioners etc., need to guarantee stability and the reliability of refrigeration agent.
When use with not chloride atom have that the global warming coefficient is low, HF hydrocarbon (hydrofluoro olefin) that have the two keys of carbon is during as the refrigeration agent of main body, has following problem.Such refrigeration agent is owing to having at high temperature labile characteristic, so when due to overcompression or expand when reaching a high temperature, easily decompose again.Therefore, such refrigeration agent, stability is low.Especially, when the medium-term and long-term use of refrigerating circulatory device at indoor air conditioner, On-vehicle air conditioner, refrigerated warehouse (refrigerator) and other air bells conditioners etc., because the decomposition of the refrigeration agent shown in high temperature occurs for a long time, so the countermeasure that need to have the temperature for refrigeration agent to rise.
In refrigeration cycle, the refrigeration agent that evaporates in vaporizer is inhaled into compressor, and by the pressure of compressor compresses to regulation.At this moment, larger change of state occurs in refrigeration agent, becomes high pressure from low pressure, becomes high temperature from low temperature.Stability and the reliability that therefore, compressing mechanism is become to guarantee refrigeration agent.
For example, patent documentation 1 is disclosed is the compressor that uses the low refrigeration agent of global warming coefficient, it begins compression for the refrigeration agent that will suck as much as possible compressor inside from low temperature, has for the direct suction path that refrigeration agent directly is supplied to suction port (port).According to such structure, to compare with the situation that is supplied to pressing chamber after refrigeration agent temporarily being stored in the storage space such as crank chamber, the temperature of the refrigeration agent before beginning to compress rises and is suppressed.Compare with the situation that refrigeration agent directly is not supplied to suction port by compressor compresses to the temperature of the pressure refrigeration agent afterwards of regulation, be suppressed owing to beginning to compress front temperature rising, so lower.So the decomposition of refrigeration agent is suppressed, the analyte (for example sludge (sludge)) that can suppress take refrigeration agent descended as the fault of the compressor of reason or life-span.That is, the reliability of compressor and durability are improved.
The look-ahead technique document
Patent documentation
Patent documentation 1: TOHKEMY 2009-228473 communique
Summary of the invention
The problem that invention will solve
Yet, even rising, the temperature of the refrigeration agent before beginning to compress is suppressed, more than the temperature of the refrigeration agent by compressor compresses to the pressure of regulation also reached and needs temperature, consequently refrigeration agent can decompose sometimes.As an one reason, " heating of expanding again " arranged." again expand heating " refers to that the refrigrant leakage that compresses the high pressure in the way expands again and reaches a high temperature to the space of low pressure in the space of low pressure, consequently the refrigeration agent of the low pressure that exists in low-voltage space heated.By such expansion again heating, the temperature that is compressed to the refrigeration agent after the pressure of regulation reach temperature required more than.In addition, when occuring to expand again heating, because use in the heating of low-temp low-pressure, so the Efficiency Decreasing of compressor the part of the compression power that consumes for the refrigeration agent that obtains High Temperature High Pressure (energy).
Compress the leakage of the refrigeration agent in the way as the method for the heating of expanding again of reason as suppressing take this, can consider, by refrigerator oil (oil) being supplied to the refrigeration agent that begins compression front (inhalation process), improve the sealing of closing refrigeration agent pressing chamber afterwards.But, exist the refrigeration agent that begins compression front (inhalation process) by the problem of the oil heating higher than refrigerant temperature.
So, in order to solve above-mentioned problem, the object of the present invention is to provide a kind of rotary compressor that uses the low refrigeration agent of global warming coefficient, it can improve the sealing of pressing chamber by using refrigerator oil, suppress the heating of expanding again, and can suppress heating, the high efficiency rotary compressor that have height reliability, durability of the refrigeration agent due to this refrigerator oil.
Be used for solving the method for problem
To achieve these goals, the present invention is constructed as follows.
In order to solve above-mentioned existing problem, according to an embodiment of the invention, a kind of rotary compressor is provided, this rotary compressor has: use the unitary system cryogen of the HF hydrocarbon with the two keys of carbon or contain the mix refrigerant of above-mentioned HF hydrocarbon, and comprise: pressing chamber, it compresses above-mentioned refrigeration agent; With the first pressing chamber fuel feeding path, it is supplied to refrigerator oil and closes above-mentioned refrigeration agent above-mentioned pressing chamber afterwards.
By being supplied to, refrigerator oil closes above-mentioned refrigeration agent above-mentioned pressing chamber afterwards, the sealing of pressing chamber is improved, thereby the heating of expansion again due to the leakage of the refrigeration agent in suppressing to compress on the way, and, supply with the refrigerating machine oil condition in the heating of the refrigeration agent due to refrigerator oil and inhalation process and compare and be suppressed.So, be compressed to the temperature of authorized pressure refrigeration agent afterwards and compare decline with supply with the refrigerating machine oil condition in inhalation process, thus, the decomposition of refrigeration agent is suppressed.
Compare with supplying with the refrigerating machine oil condition in inhalation process, when refrigerator oil is supplied to the above-mentioned pressing chamber that closes after above-mentioned refrigeration agent, be compressed to the lower reason of the temperature of the refrigeration agent after authorized pressure as follows.
The temperature that sucks the refrigeration agent of (in suction stroke) in the pressing chamber process is minimum.When such refrigeration agent is supplied with the refrigerator oil of high temperature, because the temperature difference of refrigeration agent and refrigerator oil is larger, so refrigeration agent is by heat intensive (thereby, advance widely the decomposition of refrigeration agent).In contrast to this, the refrigeration agent in compression figure is along with compression, and the temperature of refrigeration agent itself rises, so little with the temperature difference of the refrigerator oil of supplying with.Further, in the situation that be compressed near the refrigeration agent of discharging pressing, the temperature of refrigeration agent is compared higher with the temperature of the refrigerator oil of supplying with.Therefore, when the above-mentioned pressing chamber that refrigerator oil is supplied to after closing above-mentioned refrigeration agent, the heating of the refrigeration agent due to more can freezing-inhibiting machine oil.Like this, supply with refrigerator oil by the supply of avoiding the refrigerator oil in suction stroke in compression section, can suppress the heating of refrigeration agent, and can improve the sealing of closing refrigeration agent pressing chamber afterwards by refrigerator oil.Wherein, refrigerator oil is preferably being supplied with as far as possible little moment of the temperature difference of refrigeration agent.
The invention effect
According to the present invention, in rotary compressor, can use depletion of the ozone layer coefficient and the low refrigeration agent of global warming coefficient, and inhibition is as the temperature rising of the refrigeration agent of the reason of the decomposition of refrigeration agent.Consequently, can provide a kind of high efficiency rotary compressor of not only having considered earth environment but also having had height reliability, durability.
Description of drawings
Aforesaid way of the present invention and feature are by more obvious to the following description of preferred embodiment being correlated with of accompanying drawing.In the accompanying drawings:
Fig. 1 is the sectional view of eddy type (scroll) compressor of embodiments of the present invention 1.
Fig. 2 is the local amplification sectional view of compressing mechanism of the scroll compressor of mode of execution 1.
Fig. 3 means the figure of a plurality of states of rotation scroll of the scroll compressor of mode of execution 1.
Fig. 4 is the local amplification sectional view of compressing mechanism of the scroll compressor of embodiments of the present invention 2.
Fig. 5 means the figure of a plurality of states of rotation scroll of the scroll compressor of mode of execution 2.
Fig. 6 is the sectional view of the rotary compressor of embodiments of the present invention 3.
Fig. 7 is the amplification sectional view of compressing mechanism of the rotary compressor of mode of execution 3.
Fig. 8 is the assembling assumption diagram of compressing mechanism of the rotary compressor of mode of execution 3.
Fig. 9 means the figure of a plurality of states of compressing mechanism of the rotary compressor of mode of execution 3.
Embodiment
Rotary compressor of the present invention has: use the unitary system cryogen of the HF hydrocarbon with the two keys of carbon or contain the mix refrigerant of above-mentioned HF hydrocarbon, and comprise: pressing chamber, and it compresses above-mentioned refrigeration agent; With the first pressing chamber fuel feeding path, it is supplied to refrigerator oil and closes above-mentioned refrigeration agent above-mentioned pressing chamber afterwards.By using depletion of the ozone layer coefficient and the low refrigeration agent of global warming coefficient, can suppress effects on the environment of the Earth.In addition, hold labile problem when the high temperature for the unitary system cryogen (or mix refrigerant) that solves the HF hydrocarbon with the two keys of this carbon, the pressing chamber that closes after refrigeration agent is supplied with refrigerator oil.Thus, by improving the sealing of pressing chamber, the heating of expansion again due to the leakage of the refrigeration agent in compression way is suppressed, and the temperature of the refrigeration agent due to the supply of refrigerator oil rises and compares and can be suppressed with supply refrigerating machine oil condition in inhalation process (refrigeration agent closed pressing chamber before).Consequently, the temperature that is compressed to the pressure refrigeration agent afterwards of regulation is compared decline with supply with the refrigerating machine oil condition in inhalation process, and the decomposition of refrigeration agent is suppressed.And, a kind of high efficiency rotary compressor of not only having considered earth environment but also having had height reliability, durability can be provided.
Compressor also can constitute and seal off and on the first pressing chamber fuel feeding path.Optimal moment of the inhibition that the temperature of refrigeration agent that can be due to the supply of the raising of the sealing that can effectively realize pressing chamber and refrigerator oil rises and with optimal amount, refrigerator oil is supplied to pressing chamber.Thus, can be further the temperature of refrigeration agent due to the supply of reliable freezing-inhibiting machine oil rise and the leakage of refrigeration agent due to expansion again heat.
Be formed between above-mentioned fixed scroll and above-mentioned rotation scroll by fixed scroll and rotation scroll are meshed at above-mentioned pressing chamber, above-mentioned fixed scroll and above-mentioned rotation scroll have respectively in end plate and the situation as the clinch (lap) that is formed on the Vorticose wall of above-mentioned end plate, be provided with from above-mentioned store oil section and refrigerator oil be supplied at least one second pressing chamber fuel feeding path of above-mentioned pressing chamber, at least one in above-mentioned the second pressing chamber fuel feeding path is above-mentioned the first pressing chamber fuel feeding path.
Generally speaking, in the rotary compressor that has a plurality of pressing chambers and the refrigeration agent in a plurality of pressing chambers is compressed simultaneously, when the refrigrant leakage in the compression way that is compressed to high pressure to a certain degree during to the pressing chamber of low voltage side, refrigeration agent easily leaks to the pressing chamber in compression way after an operation, rather than is sucking the pressing chamber (so-called internal leakage occurs) of refrigeration agent.At this moment, the heating of the refrigeration agent in the pressing chamber that not only causes conduct leakage object that expands again of the refrigeration agent of leakage also causes the rising as the interior pressure of the pressing chamber that leaks object.Due to such internal leakage, the temperature of refrigeration agent rises.As its countermeasure, can be by at least one the second pressing chamber fuel feeding path that refrigerator oil is supplied to pressing chamber be set, use the refrigerator oil of optimal amount, improve the rise sealing of pressing chamber that the internal leakage of special contribution is arranged of the temperature that produces refrigeration agent.In addition, by using the refrigerator oil of optimal amount, also can suppress the heating due to the refrigeration agent due to the caused unnecessary refrigerator oil of the supply of the refrigerator oil of excess quantity.
In the situation that have as above-mentioned pressing chamber the clinch that is formed on above-mentioned rotation scroll the outside the first pressing chamber and be formed on second pressing chamber of inboard of the clinch of above-mentioned rotation scroll, also can make be supplied to leak in above-mentioned the first pressing chamber and above-mentioned the second pressing chamber length the delivery volume of the refrigerator oil of long pressing chamber more than the delivery volume that is supplied to another pressing chamber.Because can be used in accordingly with the length of the leak of pressing chamber the delivery volume optimization of the refrigerator oil that improves sealing, so also can suppress heating due to the refrigeration agent due to the caused remaining refrigerator oil of supply of the refrigerator oil of excess quantity.
In the situation that have as above-mentioned pressing chamber the clinch that is formed on above-mentioned rotation scroll the outside the first pressing chamber and be formed on second pressing chamber of inboard of the clinch of above-mentioned rotation scroll, also can make the delivery volume of the refrigerator oil that is supplied to the pressing chamber that in above-mentioned the first pressing chamber and above-mentioned the second pressing chamber, rate of volumetric change is higher more than the delivery volume that is supplied to another pressing chamber.Because the pressure difference of the pressing chamber of the refrigerator oil by optimal amount and low voltage side is larger, so can improve the sealing of pressing chamber of the leakage of easy generation refrigeration agent.Also can suppress the heating due to the refrigeration agent due to the caused unnecessary refrigerator oil of the supply of the refrigerator oil of excess quantity.
Above-mentioned the first pressing chamber fuel feeding path also can comprise: import road section, it is arranged at the back side of above-mentioned rotation scroll, and section imports refrigerator oil from above-mentioned store oil; For oil circuit section, its clinch that is arranged at above-mentioned rotation scroll is inner in clinch, is communicated with above-mentioned importing road section, and has opening at the clinch end face; And recess, its be arranged at above-mentioned fixed scroll end plate and with above-mentioned clinch in be communicated with off and on for the opening of oil circuit section.Thus, can be during specific to closing the pressing chamber supply refrigerator oil after refrigeration agent, and more easily carry out the adjustment of the delivery volume of refrigerator oil.In addition, also can prevent refrigeration agent adverse current to the first pressing chamber fuel feeding path after compressed, and can realize the scroll compressor (scroll compressor) of height reliability.
Refrigeration agent can comprise as a kind of tetrafluoeopropene of HF hydrocarbon and at least one in trifluoro propene, and to make the global warming coefficient be more than 5 below 750, is preferably more than 5 below 350.According to such refrigeration agent, can provide effectively that environmental loads is little, height reliability and high efficiency rotary compressor.
Refrigeration agent also can with as a kind of tetrafluoeopropene of HF hydrocarbon or trifluoro propene as main component, and so that the global warming coefficient becomes more than 5 below 750, preferably make it become more than 5 the mode below 350 and mix difluoromethane and pentafluoroethane.According to such refrigeration agent, can reduce environmental loads, weapons suppress flow velocity and temperature are descended, thus effectively body with a kind of height reliability and high efficiency rotary compressor.
As refrigerator oil can use copolymer, (4) of poly-inferior (oxygen) alkyl glycol of (1) polyoxyalkylene glycol class, (2) glymes, (3) or its monoether and polyvinylether contain the artificial oil of polyol ester and polycarbonate-based oxygenatedchemicals, (5) with alkyl benzene as the artificial oil of main component or (6) with the artificial oil of alhpa olefin class as main component.By such refrigerator oil, can effectively provide height reliability and high efficiency rotary compressor.
Below, with reference to accompanying drawing, embodiments of the present invention are described.But, and can't help present embodiment and limit the present invention.
In the compressor of three embodiments of the present invention of lifting below, use the unitary system cryogen of the HF hydrocarbon with the two keys of carbon or contain the mix refrigerant of above-mentioned HF hydrocarbon.
(mode of execution 1)
Fig. 1 is the longitudinal section of eddy type (scroll) compressor of embodiments of the present invention 1, and Fig. 2 is the local amplification sectional view of the compressing mechanism of scroll compressor as shown in Figure 1, and Fig. 3 means the figure of a plurality of states of the rotation scroll of compressing mechanism.Below, the work of scroll compressor, effect are described.
As shown in Figure 1, the scroll compressor of present embodiment 1 has seal container 1.Scroll compressor also has compressing mechanism 2, motor section 3 and store oil section 20 in the inside of seal container 1.Compressing mechanism 2 comprises: the main bearing parts 11 that are fixed in seal container 1 by welding or shrunk fit etc.; By the axle 4 of these main bearing parts 11 supportings; Be fixed on fixed scroll 12 on main bearing parts 11 by bolt etc.; And be configured between main bearing parts 11 and fixed scroll 12 and with the rotation scroll 13 of fixed scroll 12 engagements.
Fixed scroll 12 comprises end plate 12a; With as being formed at clinch (lap) 12b of the Vorticose wall of end plate 12a, rotation scroll 13 comprises end plate 13a; With as being formed at the clinch 13b of the Vorticose wall of end plate 13a.Be provided with rotation limting mechanism 14 between rotation scroll 13 and main bearing parts 11, this rotation limting mechanism 14 comprises Othemos ring (Oldham ring, cross slip-ring) etc., this Othemos ring prevents from rotating the rotation of scroll 13, and so that the rotation scroll 13 that is driven by axle 4 guide by the mode of circular orbit motion.The eccentric axial portion 4a of the upper end by being positioned at axle 4 makes rotation scroll 13 eccentric rotaries, realizes rotating the rotatablely moving of circular orbit of scroll 13.
According to such structure, dwindle volume from outer circumferential side to center side and move while be formed on fixed scroll 12 and the pressing chamber 15 of rotation between scroll 13.The suction port 17 of the suction pipe 16 that is communicated with via the outside with seal container 1 and the peripheral part of fixed scroll 12, refrigeration agent (gas) are inhaled in pressing chamber 15 (inhalation process).Carry out the compression (compression section) of refrigeration agent by (after refrigeration agent is closed pressing chamber 15) after the closes compression chamber 15 of rotatablely moving of rotation scroll 13.Reach the refrigeration agent of authorized pressure by compression, push the leaf valve 19 at tap hole 18 places of the central part that is arranged at fixed scroll 12 open, via tap hole 18, move in seal container 1 from pressing chamber 15.
In addition, the other end at axle 4 is provided with pump 25.Pump 25 is configured to that suction port is positioned at and is arranged at the store oil section 20 of the bottom of seal container 1.Pump 25 and compressing mechanism 2 synchronous drive, thus pump 25 can with pressure condition or movement velocity irrespectively, the refrigerator oil (oil) 6 that will be housed in reliably in store oil section 20 drinks up, and can stably be supplied to compressing mechanism 2.The oil 6 that this pump 25 drinks up is supplied to compressing mechanism 2 by the oily supply hole 26 of through shaft 4 inside.Wherein, by utilize pump 25 drink up before or drink up after utilize oil strainer etc. to remove foreign matter in oil 6, can prevent that foreign matter from sneaking into compressing mechanism 2, thereby can realize the further raising of the reliability of compressor.
The pressure of the oil 6 of importing compressing mechanism 2 and the head pressure of scroll compressor are roughly the same, so become the back pressure source to rotation scroll 13.That is, oil 6 plays the back side (face relative with main bearing parts 11) of pressing rotation scroll 13, rotation scroll 13 is pressed into the effect of fixed scroll 12.Thus, rotation scroll 13 can not left fixed scroll 12, can not contact with fixed scroll 12 locally yet, maintains the state that contacts with fixed scroll 12.Thereby compressing mechanism 2 can be stablized the compressed capability of performance regulation.Further, an oil part of 6 press by supplys or own wt enter eccentric axial portion 4a and rotate the embedding part of scroll 13 and be arranged at axle 4 and main bearing parts 11 between bearing portion 66, be lubricated.Oil 6 after lubricated as shown in the arrow of Fig. 2, drips and returns store oil section 20.
In addition, between the back side and main bearing parts 11 that sealed member 78 are configured in rotation scroll 13, delimit high-pressure area 30 in the inboard of sealed member 78, delimit back pressure chamber 29 in the outside of sealed member 78.Due to the pressure of the pressure that can separate high-pressure area 30 fully and back pressure chamber 29, so can stablize the pressure of controlling the back side of rotation scroll 13.
The a part of 12c of end plate 12a between the clinch 12b of fixed scroll 12 is formed with recess 12d.In addition, at rotation scroll 13 places, be formed with in clinch for oil circuit 55.Be communicated with back pressure chamber 29 via opening 55a on one side for oil circuit 55 in clinch.And back pressure chamber 29 is via the importing road 54 of the back side that is arranged at rotation scroll 13 and be arranged at oily supply hole 26 in axle 4, is communicated with store oil section 20.On the other hand, be formed on end face with the clinch 13a of the end plate 12a sliding contact of fixed scroll 12 for the opening 55b of the another side of oil circuit 55 in clinch.For the opening 55b of oil circuit 55, as shown in the dotted line of Fig. 3, by rotatablely moving of rotation scroll 13, to draw the mode of circular rotating locus, with respect to fixed scroll 12, relatively move in this clinch.
Fig. 3 represents a plurality of states with the rotation scroll 13 of fixed scroll 12 engagement, particularly, represents that each phase place diverges to the state of the rotation scroll 13 of 90 degree.As shown in Figure 3, as the pressing chamber 15 that is formed by fixed scroll 12 and rotation scroll 13, comprise the first pressing chamber 15a and the second pressing chamber 15b that is formed on the inboard of clinch 13a in the outside of the clinch 13a that is formed on rotation scroll 13.The first pressing chamber 15a, the second pressing chamber 15b are respectively by rotating rotatablely moving of scroll 13, while dwindle volume to central mobile.When the refrigeration agent in pressing chamber 15 reached head pressure and pressing chamber 15 and is communicated with tap hole 18, the refrigeration agents in pressing chamber 15 were pushed leaf valve 19 open, move to discharge in chamber 31.
As shown in Figure 3, in clinch, the opening 55b for oil circuit 55 is communicated with off and on the recess 12d of a part of 12c of the end plate 12a that is formed on fixed scroll 12.Thus, be communicated with off and on via recess 12d with the second pressing chamber 15b for oil circuit 55 in clinch.
Below, be conceived to the second pressing chamber 15b and describe.As shown in Fig. 3 (a), outermost the second pressing chamber 15b that is formed on rotation scroll 13 is communicated with suction port 17, and refrigeration agent begins to import (beginning inhalation process) to the second pressing chamber 15b.And, as shown in Fig. 3 (c), close the second pressing chamber 15b by rotatablely moving of scroll 13 of rotation, refrigeration agent is just closed in the second pressing chamber 15b (beginning compression section).Afterwards, as shown in Fig. 3 (d), by rotatablely moving of rotation scroll 13, opening 55b for oil circuit 55 in clinch is communicated with the second pressing chamber 15b via recess 12d, and, via from back pressure chamber 29, oil 6 is supplied to the second pressing chamber 15b of closing after refrigeration agent in clinch for oil circuit 55.In contrast, as Fig. 3 (a)～(c), when opening 55b is not communicated with recess 12d, hardly oil is supplied to the second pressing chamber 15b from back pressure chamber 29.Like this, be communicated with off and on via the recess 12d of fixed scroll 12 by making in clinch for the opening 55b of oil circuit 55 and the second pressing chamber 15b, oil 6 is via being supplied to off and on the second pressing chamber 15b for oil circuit 55 in clinch.Wherein, to oil 6 reasons that are supplied to the second pressing chamber 15b are narrated in the back.
As mentioned above, according to present embodiment 1, by using the depletion of the ozone layer coefficient and the global warming coefficient is little, unitary system cryogen HF hydrocarbon or contain the mix refrigerant of above-mentioned HF hydrocarbon, can suppress effects on the environment of the Earth.In addition, by oil 6 being supplied to the second pressing chamber 15b that closes (compression section) after refrigeration agent, supply the situation of oil supply 6 to compare reduction in the temperature that is compressed to the refrigeration agent after authorized pressure and inhalation process (state that namely is communicated with suction port 17).
The temperature of the refrigeration agent of (in suction stroke) is minimum in sucking the second pressing chamber 15b way.When such refrigeration agent was supplied with the oil 6 of high temperature, refrigeration agent was large with the temperature difference of oil 6, so refrigeration agent is by heat intensive (consequently, promoting widely the decomposition of refrigeration agent).In contrast, the refrigeration agent in compression way is accompanied by compression, the temperature rising of refrigeration agent itself, so with the having a narrow range of temperature of the oil 6 of supplying with.Further, discharge the refrigeration agent of pressing in the situation that be compressed into to approach, the temperature that the temperature of refrigeration agent compares the oil 6 of supplying with is high.Thereby, oil 6 is supplied to the situation that closes the second pressing chamber 15b of (compression section) after refrigeration agent, more can suppress the heating of the refrigeration agent due to oil 6.Like this, supply oil supply 6 by the supply of avoiding the oil 6 in suction stroke in compression section, can suppress the heating of refrigeration agent, and improve the sealing of closing refrigeration agent the second pressing chamber 15b afterwards by oil 6.Wherein, oil 6 is preferably being supplied with as far as possible little moment of the temperature difference of refrigeration agent.
Secondly, reach between clinch 12b and end plate 13a between end plate 12a by oil 6 second pressing chamber 15b(fixed scroll 12 and the clinch 13b of rotation scroll 13) sealing be improved, so can suppress the heating of expanding again, that is to say the leakage that can suppress from the refrigeration agent of the second pressing chamber 15b.
Consequently, the temperature of refrigeration agent rises and is suppressed, and the decomposition of refrigeration agent also is suppressed.And, a kind of high efficiency rotary compressor of not only having considered earth environment but also having had height reliability, durability can be provided.
Again secondly, can be with the oil 6 at the back side of rotation scroll 13 when rotation scroll 13 be specific phase place (, axle 4 for specific angle of swing time) via supplying oil circuit 55 and recess 12d to be supplied to the second pressing chamber 15b in clinch.That is optimal opportunity of the inhibition that the temperature of refrigeration agent that, can be due to the supply of the raising of the sealing that can effectively realize the second pressing chamber 15b and oil 6 rises and oil 6 is supplied to the second pressing chamber 15b with optimal amount.The temperature that thus, can further suppress reliably the refrigeration agent due to oil 6 supply rise and the leakage of refrigeration agent due to expansion again heat.
Begin thus to illustrate via for oil circuit 55, oil 6 being supplied to the reason of the second pressing chamber 15b in clinch.At first, the shape of the clinch that fixed scroll 12 and rotation scroll 13 have is described.In the present embodiment, the vortex shape of the clinch of fixed scroll and rotation scroll is by gradually opening (involute) curve definitions.If the involute angle is made as θ, Base radius is made as a, involute curve in cartesian coordinate system by following function representation.
(formula 1)
x=a(cosθ+θsinθ)
y=a(sinθ+θcosθ)
Curve by formula 1 expression is made as datum curve.In the middle of described two envelopes of datum curve when turning radius ε rotates, the envelope in the outside is by following function representation.
(formula 2)
x=a(cos(θ-ε/a)+θsin(θ-ε/a))
y=a(sin(θ-ε/a)+θcos(θ-ε/a))
Equally, inboard envelope is by following function representation.
(formula 3)
x=a(cos(θ+ε/a)+θsin(θ+ε/a))
y=a(sin(θ+ε/a)+θcos(θ+ε/a))
By by any the outer surface of clinch in the function definition fixed scroll 12 of above-mentioned datum curve (reference curve) or rotation scroll 13, by the internal surface of another clinch of the function definition of above-mentioned outside envelope and its combination, a plurality of smallest radials gap of the outer surface side of a plurality of smallest radials gap of the clinch inner surface side of clinch 13b that form simultaneously, rotation scroll 13 with the clinch engagement of rotation scroll by making fixed scroll or the clinch 13b of rotation scroll 13 becomes and equates.In the present embodiment, realize asymmetrical pressing chamber 15 by the clinch 12b that forms fixed scroll 12 in the different mode of winding number and the clinch 13b that rotates scroll 13, realize thus the expansion of the volume of pressing chamber 15.
In order to form asymmetrical pressing chamber, the rate of volumetric change of the second pressing chamber 15b of inner surface side that is formed on the clinch 13b of rotation scroll 13 is compared larger with the rate of volumetric change of the first pressing chamber 15a of the outer surface side that is formed on clinch 13b.In the second larger pressing chamber 15b of rate of volumetric change, the pressure of refrigeration agent is compared with the first pressing chamber 15a more sharp and to be risen, so increase with the pressure difference of the pressing chamber 15 of low voltage side.Therefore, easily leak by the refrigeration agent of the pressing chamber that flows to low voltage side 15 between clinch and end plate from the second pressing chamber 15b, need to improve sealing.
So in present embodiment 1, the second pressing chamber 15b larger to rate of volumetric change suitably arranges in clinch for oil circuit 55 and recess 12d, to supply with more oily 6.Thus, the leakage of refrigeration agent that flows to the pressing chamber 15 of low voltage side from the second pressing chamber 15b is suppressed, thereby the heating of expansion again of the refrigeration agent in the pressing chamber 15 of low voltage side is suppressed, and can suppress the pressure rise due to internal leakage.Consequently, the temperature of holding the refrigeration agent that uses in the scroll compressor of labile, present embodiment 1 under high temperature rises and is suppressed.
Wherein, also can be provided for oil 6 is supplied to the other pressing chamber fuel feeding path (the second pressing chamber fuel feeding path except the first pressing chamber fuel feeding path) of the first pressing chamber 15a, the oil 6 that will compare with the amount of the oil 6 that is supplied to off and on the second pressing chamber 15b less amount is supplied to the first pressing chamber 15a via other pressing chamber fuel feeding path.Other pressing chamber fuel feeding path as such for example is provided with pressing chamber fuel feeding path 57 as shown in Figure 2.Pressing chamber fuel feeding path 57 is formed at rotation scroll 13.In addition, the opening on one side of pressing chamber fuel feeding path 57 is formed on the end face of clinch 13b.The opening of another side via the importing road 54 at the back side that is arranged on rotation scroll 13, be arranged on the oily supply hole 26 at axle 4 places etc., be communicated with store oil section 20.Thus, can be from the end plate 12a of fixed scroll 12 and the oil 6 of the some amounts of gap supply of the end face of the clinch 13b of rotation scroll 13.
At this moment, also can suppress the heating of expansion again to refrigeration agent, and can suppress the pressure rise due to internal leakage.In addition, the delivery volume of the oil 6 of supplying with to the second higher pressing chamber 15b of rate of volumetric change is compared more with the delivery volume of supplying with to the first pressing chamber 15a, thus can utilize the oil of optimal amount improve due to the sealing of the pressing chamber of the leakage of the large and incidental refrigeration agent of pressure difference of the pressing chamber 15 of low voltage side.Thus, can suppress also that refrigerator oil by the excess supply amount is that cause, the heating of the refrigeration agent due to unnecessary refrigerator oil.
In addition, be supplied to the second pressing chamber 15b oil 6 amount with close refrigeration agent after the amount of (the second pressing chamber 15b close after) oil of supplying with compare the oil of less amount, also can be at refrigeration agent by (the second pressing chamber 15b begin to close before) before closing or when closing refrigeration agent (close to since the second pressing chamber 15b close fully during) supply with.That is, as long as the major part of the amount of required oil 6 is supplied with after closing refrigeration agent, the temperature that just can suppress refrigeration agent rises, is the decomposition of refrigeration agent.
(mode of execution 2)
Fig. 4 is the local amplification sectional view of compressing mechanism of the scroll compressor of embodiments of the present invention 2.Fig. 5 means the figure of a plurality of states of rotation scroll.Structure member beyond pressing chamber fuel feeding path 56 is identical with above-mentioned mode of execution 1.In Fig. 4, Fig. 5, to the structure member mark identical symbol identical with Fig. 2, Fig. 3.In addition, only carry out the explanation to pressing chamber fuel feeding path 56, the explanation of omitting other structure member.
As shown in Figure 4, in the scroll compressor of present embodiment 2, pressing chamber fuel feeding path 56 is formed at the end plate 13a of rotation scroll 13.In addition, pressing chamber fuel feeding path 56 makes back pressure chamber 29 be communicated with the first pressing chamber 15a of the outer surface side of the clinch 13b that is formed on rotation scroll 13.Yet, pressing chamber fuel feeding path 56 rotation scroll 13 be in as Fig. 5 (b) thus as shown in state the time be communicated with the first pressing chamber 15a oil 6 be supplied to the first pressing chamber 15a, but, be in Fig. 5 (a), 5(c), 5(d) shown in state the time, the supply to the oil 6 of the first pressing chamber 15a is not carried out in the end plate 12a sealing of the scroll that is fixed 12.The scroll compressor that dwindles along with the volume from outer circumferential central mobile pressing chamber, the volume of pressing chamber that the volume ratio that is positioned at the pressing chamber in the outside is positioned at center side is large.Therefore, the leakage length of the length in the place of just leaking as the pressing chamber of refrigeration agent from the less on high-tension side pressing chamber of volume to the larger low voltage side of volume (in other words, required seal length), the ratio of the first pressing chamber 15a in the outside that is formed on the clinch 13b of rotation scroll 13 is formed on the length of the second inboard pressing chamber 15b.Therefore, by to leaking the first long pressing chamber 15a of length, supply with than the amount of the oil 6 that is supplied to the second pressing chamber 15b oil 6 of volume more via pressing chamber fuel feeding path 56, leak length the first pressing chamber 15a of length fully sealed.Thus, suppress the temperature rising that high temperature holds labile refrigeration agent.
According to present embodiment 2, due to the pressure rise due to expand again heating and the internal leakage that can suppress refrigeration agent, and due to can by make to leak length the oil 6 of the first long pressing chamber 15a delivery volume with compare more to the delivery volume of the second pressing chamber 15b, be used in accordingly the fuel delivery optimization of the oil 6 that improves sealing with the length of the leak of pressing chamber, so can suppress also that refrigerator oil by the excess supply amount is that cause, the heating of the refrigeration agent due to unnecessary refrigerator oil.
(mode of execution 3)
Fig. 6 is the longitudinal section of the rotary compressor of embodiments of the present invention 3.Fig. 7 is the amplification sectional view of the compressing mechanism of rotary compressor.Fig. 8 is the assembling assumption diagram of the compressing mechanism of rotary compressor.And Fig. 9 means the figure of a plurality of states of the compressing mechanism of rotary compressor.As shown in Figure 6 and Figure 7, in rotary compressor, motor 102 and compressing mechanism 103 are accommodated in seal container 101 with the state that links via crankshaft (crank shaft) 131.Compressing mechanism 103 has: cylinder 130; Suction chamber 149 and pressing chamber 139, it is formed by the end plate 134 of the upper side bearing 134a of the both ends of the surface of the above-mentioned cylinder 130 of sealing and the end plate 135 of lower side bearing 135a; Piston 132, it is configured in cylinder interior 130; And blade (vane) 133, its outer circumferential face with piston 132 contacts and cylinder 130 is divided into suction chamber 149 and pressing chamber 139.Piston 132 is with chimeric by the eccentric part 131a of the crankshaft 131 of side bearing 134a and lower side bearing 135a supporting, by crankshaft 131 eccentric rotaries.Blade 133 is in order to keep and the contacting of the outer circumferential face of the piston 132 of eccentric rotary, constitute with the eccentric rotary of piston 132 correspondingly, to piston 132 to-and-fro motion.
At crankshaft 131 places, be formed with from store oil section 20 draw oil, along the oilhole 141 of central shaft.With the part of upper side bearing 134a, crankshaft 131 that lower side bearing 135a is relative, be provided with the oil supply hole 142,143 that is communicated with oilhole 141 respectively.In addition, the part relative with piston 132 at the eccentric part 131a of crankshaft 131 is formed with the oil supply hole 144 that is communicated with oilhole 141 and the oil groove 145 that is communicated with oil supply hole 14.
On the other hand, at cylinder 130, be formed with the suction port 140 that is drawn into suction chamber 149 for the refrigeration agent with gaseous state.When the sliding contacting part with the piston 132 of the inner peripheral surface sliding contact of cylinder 130 left suction port 140 by suction port 140, suction chamber 149 slowly enlarged, and thus, refrigeration agent is inhaled in suction chamber 149 from suction port 140.At upper side bearing 134a, open the exhaust port 138 that is useful on from pressing chamber 139 discharging refrigerants.Exhaust port 138 forms as the hole with circular cross-section that connects upper side bearing 134a.At the upper surface of exhaust port 138, the expulsion valve 136 of opening when being provided with the pressure more than being subject to authorized pressure and the cup type silencing apparatus (cup muffler) 137 that covers this expulsion valve 136.
Along with the slide part of the piston 132 of the inner peripheral surface sliding contact of cylinder 130 near exhaust port 138, pressing chamber 139 slowly dwindles.When the refrigerant compression in pressing chamber 139 was above to authorized pressure, expulsion valve 136 was opened.When expulsion valve 136 was opened, refrigeration agent flowed out and is discharged in seal container 101 by cup type silencing apparatus 137 from exhaust port 138.
On the other hand, formation has: the space 146 that is surrounded by the inner peripheral surface of the end plate 134 of the eccentric part 131a of crankshaft 131, upper side bearing 134a and piston 132; The space 147 that surrounds with inner peripheral surface by the end plate 135 of the eccentric part 131a of crankshaft 131, lower side bearing 135a and piston 132.Oil from oilhole 141 via oil supply hole 142, the 143 above-mentioned space 146,147 of bleeding.This space 146,147 pressure are roughly always high than the pressure in pressing chamber 139, substantially equate with head pressure.
In addition, the height setting of cylinder 130 is that the height than piston 132 is large a little, so that piston 132 can be in the slides within of cylinder 130.Therefore, gapped between the end plate 135 of the end plate 134 of the end face of this piston 132 and upper side bearing 134a, lower side bearing 135a.Oil in space 146,147 bleeds via this gap in pressing chamber 139.
In the rotary compressor that consists of as described above, as shown in Figure 8, be provided with the pressing chamber fuel feeding path 155 of recess shape at the end plate 135 of lower side bearing 135a.That Fig. 9 represents to observe from the central axis direction of crankshaft 131, piston 132 and position relationship for oil circuit 155.Shown in the lower-left of Fig. 9, when the entrance 155a of pressing chamber fuel feeding path 155 is communicated with the inboard of piston 132, outlet 155b at pressing chamber fuel feeding path 155 is that be communicated with pressing chamber 139, the interval of the degree in crank angle of crankshaft 131, and pressing chamber 139 is carried out fuel feeding.Different from the angular orientation at the crankshaft center of outlet 155b with respect to entrance 155a by pressing chamber fuel feeding path 155 is set to, can determine that oil flows into the interval of the degree in crank angle of entrance 155a.Thus, the degrees of freedom of the position of outlet 155b increases.The outlet 155b of pressing chamber fuel feeding path 155 consequently, can be set near the position of refrigrant leakage.
In addition, shown in Fig. 9 lower-left, be arranged near the position point of contact of piston 132 and cylinder 130 in pressing chamber 139 by the outlet 155b with pressing chamber 155, can be with the oil inhibition of the required minimum flow leakage via the refrigeration agent between piston 132 and cylinder 130.Thus, suppress the temperature rising that high temperature holds labile refrigeration agent.
According to present embodiment 3, by using depletion of the ozone layer coefficient and the low refrigeration agent of global warming coefficient, can suppress effects on the environment of the Earth.In addition, by supplying oil supply to closing refrigeration agent pressing chamber 139 afterwards, the expansion again of refrigeration agent heating is suppressed, and the heating of the refrigeration agent due to refrigerator oil is compared with inhalation process (before refrigeration agent is closed pressing chamber) supply refrigerating machine oil condition and is suppressed.Consequently, the decomposition of refrigeration agent is suppressed.
Above, the rotary compressor of mode of execution 1～3 has been described.In the rotary compressor of mode of execution 1～3, use the unitary system cryogen of the HF hydrocarbon with the two keys of carbon or contain the mix refrigerant of above-mentioned HF hydrocarbon.As this mix refrigerant, also can use the refrigeration agent that mixes HF hydrocarbon and do not have the hydrogen fluorohydrocarbon of the two keys of carbon.
In addition, also can use a kind of tetrafluoeopropene (HFO1234yf or HFO1234ze) as HF hydrocarbon or trifluoro propene (HFO1243zf) and mix refrigerant as a kind of difluoromethane (HFC32) of hydrogen fluorohydrocarbon.
Secondly, also can use a kind of tetrafluoeopropene (HFO1234yf or HFO1234ze) as HF hydrocarbon or trifluoro propene (HFO1243zf) and mix refrigerant as a kind of pentafluoroethane (HFC125) of hydrogen fluorohydrocarbon.
Again secondly, also can use a kind of tetrafluoeopropene (HFO1234yf or HFO1234ze) as HF hydrocarbon or trifluoro propene (HFO1243zf) with as a kind of pentafluoroethane (HFC125) of hydrogen fluorohydrocarbon and difluoromethane (HFC32) is that mix, mix refrigerant that comprise three kinds of compositions.
And above-mentioned mix refrigerant is preferably take the global warming coefficient as more than 5 below 750, is preferably the mode below 350 more than 5, respectively two kinds of compositions or three kinds of compositions is mixed.
In addition, refrigerator oil as rotary compressor of the present invention uses is preferably: artificial oil, (5) artificial oil or (6) artificial oil take the alhpa olefin class as main component take alkyl benzene as main component of polyol ester and polycarbonate-based oxygenatedchemicals contained in copolymer, (4) of poly-inferior (oxygen) alkyl glycol of (1) polyoxyalkylene glycol class, (2) glymes, (3) or its monoether and polyvinylether.
In the present invention, fully to preferred embodiment being illustrated, still very clear and definite to those skilled in the art with reference to accompanying drawing, can cross it is made various distortion and correction.Be appreciated that those distortion and modification, only otherwise break away from the scope of the present invention of the scope of additional application, just be contained in wherein.
The disclosure that the Japan of on September 27th, 2010 application speciallys permit out specification, accompanying drawing and the claim of No. the 2010-214877th, hope (Japanese patent application) all writes among this specification as a reference.
Utilize possibility on industry
As mentioned above, according to the present invention, when use have the two keys of carbon HF hydrocarbon the unitary system cryogen or when containing the mix refrigerant of above-mentioned HF hydrocarbon, rotary compressor also can be realized height reliability, high durability and high efficiency.Therefore, the present invention can be applicable to have the purposes such as air conditioner, heat pump water heater, freezing-cooling storeroom, dehumidifier of rotary compressor.
The reference numeral explanation
12 fixed scroll
The 12a end plate
The 12b clinch
The 12d recess
13 rotation scroll
The 13a end plate
The 13b clinch
14 rotation limting mechanisms
15 pressing chambers
15a the first pressing chamber
15b the second pressing chamber
17 suction ports
18 tap holes
19 leaf valves
20 store oil sections
29 back pressure chambers
30 high-pressure areas
Supply oil circuit in 55 clinchs
56 pressing chamber fuel feeding paths
130 cylinders
131 bent axles
133 blades
The 134a upper bearing (metal)
The 135a lower bearing
139 pressing chambers
141 oilholes
155 pressing chamber fuel feeding paths
Claims (9)
1. rotary compressor is characterized in that:
Use have the two keys of carbon HF hydrocarbon the unitary system cryogen or contain the mix refrigerant of described HF hydrocarbon, and comprise:
Pressing chamber, it compresses described refrigeration agent; With
The first pressing chamber fuel feeding path, it is supplied to refrigerator oil and closes described refrigeration agent described pressing chamber afterwards.
2. rotary compressor as claimed in claim 1 is characterized in that:
Constitute and seal off and on described the first pressing chamber fuel feeding path.
3. rotary compressor as claimed in claim 1 or 2 is characterized in that:
Described pressing chamber is by being formed between described fixed scroll and described rotation scroll fixed scroll and the engagement of rotation scroll, described fixed scroll and described rotation scroll have respectively end plate and as being formed on the clinch of the Vorticose wall of described end plate
And have:
The store oil section of storage refrigerator oil; With
Section is supplied to refrigerator oil at least one second pressing chamber fuel feeding path of described pressing chamber from described store oil,
At least one in described the second pressing chamber fuel feeding path is described the first pressing chamber fuel feeding path.
4. rotary compressor as claimed in claim 3 is characterized in that:
Have as described pressing chamber:
The first pressing chamber that forms in the outside of the clinch of described rotation scroll; With
The second pressing chamber that forms in the inboard of the clinch of described rotation scroll, and
Make the delivery volume of the refrigerator oil that is supplied to the pressing chamber that in described the first pressing chamber and described the second pressing chamber, leakage length is grown more than the delivery volume that is supplied to another pressing chamber.
5. rotary compressor as described in claim 3 or 4 is characterized in that:
Have as described pressing chamber:
The first pressing chamber that forms in the outside of the clinch of described rotation scroll; With
The second pressing chamber that forms in the inboard of the clinch of described rotation scroll, and
Make the delivery volume of the refrigerator oil that is supplied to the pressing chamber that in described the first pressing chamber and described the second pressing chamber, rate of volumetric change is higher more than the delivery volume that is supplied to another pressing chamber.
6. rotary compressor as described in any one in claim 3～5 is characterized in that:
Described the first pressing chamber fuel feeding path comprises:
Import road section, it is arranged at the back side of described rotation scroll, and section imports refrigerator oil from described store oil;
For oil circuit section, its clinch that is arranged at described rotation scroll is inner in clinch, is communicated with described importing road section, and has opening at the clinch end face; With
Recess, its be arranged at described fixed scroll end plate and with described clinch in be communicated with off and on for the opening of oil circuit section.
7. rotary compressor as described in any one in claim 1～6 is characterized in that:
Described refrigeration agent comprises as a kind of tetrafluoeopropene of HF hydrocarbon and at least one in trifluoro propene, and to make the global warming coefficient be more than 5 below 750, is preferably more than 5 below 350.
8. rotary compressor as described in any one in claim 1～6 is characterized in that:
Described refrigeration agent with as a kind of tetrafluoeopropene of HF hydrocarbon or trifluoro propene as main component, and so that the global warming coefficient becomes more than 5 below 750, preferably make it become more than 5 the mode below 350 and mix difluoromethane and pentafluoroethane.
9. rotary compressor as described in any one in claim 1～8 is characterized in that:
As described refrigerator oil can use copolymer, (4) of poly-inferior (oxygen) alkyl glycol of (1) polyoxyalkylene glycol class, (2) glymes, (3) or its monoether and polyvinylether contain the artificial oil of polyol ester and polycarbonate-based oxygenatedchemicals, (5) with alkyl benzene as the artificial oil of main component or (6) with the artificial oil of alhpa olefin class as main component.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2010-214877 | 2010-09-27 | ||
| JP2010214877 | 2010-09-27 | ||
| PCT/JP2011/005395 WO2012042825A1 (en) | 2010-09-27 | 2011-09-26 | Rotary compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103154521A true CN103154521A (en) | 2013-06-12 |
Family
ID=45892317
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011800466082A Pending CN103154521A (en) | 2010-09-27 | 2011-09-26 | Rotary compressor |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20130189080A1 (en) |
| JP (1) | JPWO2012042825A1 (en) |
| CN (1) | CN103154521A (en) |
| WO (1) | WO2012042825A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2014206334A1 (en) * | 2013-06-27 | 2014-12-31 | Emerson Climate Technologies, Inc. | Scroll compressor with oil management system |
| CN104047849B (en) * | 2014-07-03 | 2017-01-18 | 湖南联力精密机械有限公司 | Vortex air compressor with built-in lubricating oil path |
| WO2016173319A1 (en) | 2015-04-30 | 2016-11-03 | 艾默生环境优化技术(苏州)有限公司 | Scroll compressor |
| WO2017168672A1 (en) * | 2016-03-31 | 2017-10-05 | 三菱電機株式会社 | Scroll compressor and refrigeration cycle device |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06167287A (en) * | 1992-12-01 | 1994-06-14 | Hitachi Ltd | Rotary compressor |
| JPH1037868A (en) * | 1996-07-19 | 1998-02-13 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| US6102671A (en) * | 1997-09-04 | 2000-08-15 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| JP2003172276A (en) * | 2001-12-03 | 2003-06-20 | Hitachi Ltd | Scroll fluid machine |
| WO2009130878A1 (en) * | 2008-04-22 | 2009-10-29 | パナソニック株式会社 | Scroll compressor |
| WO2010047116A1 (en) * | 2008-10-22 | 2010-04-29 | パナソニック株式会社 | Cooling cycle device |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS59185892A (en) * | 1983-04-05 | 1984-10-22 | Toyoda Autom Loom Works Ltd | Scroll type compressor |
| JPH06346878A (en) * | 1993-06-04 | 1994-12-20 | Hitachi Ltd | Rotary compressor |
| CN1273746C (en) * | 1997-09-17 | 2006-09-06 | 三洋电机株式会社 | Scroll compressor having a discharge port |
| JP5592597B2 (en) * | 2008-03-17 | 2014-09-17 | Ｊｘ日鉱日石エネルギー株式会社 | Refrigerator oil and working fluid composition for refrigerator |
| JP5304285B2 (en) * | 2009-02-03 | 2013-10-02 | パナソニック株式会社 | Scroll compressor |
-
2011
- 2011-09-26 JP JP2012516405A patent/JPWO2012042825A1/en active Pending
- 2011-09-26 WO PCT/JP2011/005395 patent/WO2012042825A1/en active Application Filing
- 2011-09-26 US US13/824,694 patent/US20130189080A1/en not_active Abandoned
- 2011-09-26 CN CN2011800466082A patent/CN103154521A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06167287A (en) * | 1992-12-01 | 1994-06-14 | Hitachi Ltd | Rotary compressor |
| JPH1037868A (en) * | 1996-07-19 | 1998-02-13 | Matsushita Electric Ind Co Ltd | Scroll compressor |
| US6102671A (en) * | 1997-09-04 | 2000-08-15 | Matsushita Electric Industrial Co., Ltd. | Scroll compressor |
| JP2003172276A (en) * | 2001-12-03 | 2003-06-20 | Hitachi Ltd | Scroll fluid machine |
| JP4075979B2 (en) * | 2001-12-03 | 2008-04-16 | 株式会社日立製作所 | Scroll fluid machinery |
| WO2009130878A1 (en) * | 2008-04-22 | 2009-10-29 | パナソニック株式会社 | Scroll compressor |
| WO2010047116A1 (en) * | 2008-10-22 | 2010-04-29 | パナソニック株式会社 | Cooling cycle device |
Also Published As
| Publication number | Publication date |
|---|---|
| US20130189080A1 (en) | 2013-07-25 |
| JPWO2012042825A1 (en) | 2014-02-03 |
| WO2012042825A1 (en) | 2012-04-05 |
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Application publication date: 20130612 |