CN1818390B - Compressor used in refrigerant cycling device - Google Patents

Compressor used in refrigerant cycling device Download PDF

Info

Publication number
CN1818390B
CN1818390B CN 200610056767 CN200610056767A CN1818390B CN 1818390 B CN1818390 B CN 1818390B CN 200610056767 CN200610056767 CN 200610056767 CN 200610056767 A CN200610056767 A CN 200610056767A CN 1818390 B CN1818390 B CN 1818390B
Authority
CN
China
Prior art keywords
refrigerant
compression assembly
compressor
oil
rotation compression
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
Application number
CN 200610056767
Other languages
Chinese (zh)
Other versions
CN1818390A (en
Inventor
松本兼三
里和哉
山口贤太郎
藤原一昭
山中正司
山崎晴久
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanyo Electric Co Ltd
Original Assignee
Sanyo Electric Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2002253225A external-priority patent/JP2004092469A/en
Priority claimed from JP2002265542A external-priority patent/JP2004101114A/en
Priority claimed from JP2002268321A external-priority patent/JP4118109B2/en
Priority claimed from JP2002272986A external-priority patent/JP4107926B2/en
Priority claimed from JP2002275172A external-priority patent/JP3995570B2/en
Priority claimed from JP2002283956A external-priority patent/JP2004116957A/en
Application filed by Sanyo Electric Co Ltd filed Critical Sanyo Electric Co Ltd
Publication of CN1818390A publication Critical patent/CN1818390A/en
Application granted granted Critical
Publication of CN1818390B publication Critical patent/CN1818390B/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

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
    • F04C18/30—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
    • F04C18/3562—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—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 the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide

Abstract

A refrigerant cycling device and a compressor in the refrigerant cycling device. The refrigerant cycle apparatus can prevent damage caused by liquid compression of a compressor without providing a receiver tank in a transition critical supercritical pressure on the high pressure side. A refrigerant cycling device, wherein a compressor comprises an electric motor element, a first and a second rotary compression elements in a sealed container. The first and the second rotary compression elements are driven by the electric motor element. The refrigerant compressed and discharged by the first rotary compression element is compressed by absorbing into the second rotary compression element, and is discharged to the gas cooler. The refrigerant cycling device comprises an intermediate cooling loopfor radiating heat of the refrigerant discharged from the first rotary compression element by using the gas cooler; a first internal heat exchanger, for exchanging heat between the refrigerant comingout of the gas cooler from the second rotary compression element and the refrigerant coming out of the evaporator; and a second internal heat exchanger, for exchanging heat between the refrigerant coming out of the gas cooler from the intermediate cooling loop and the refrigerant coming out of the first internal heat exchanger from the evaporator.

Description

Be used in the compressor of cooling circulation device
Technical field
The invention relates to a kind of conversion critical cooling circulation device (transcriticalrefrigerant device), it possesses the formation that compressor, gas cooler (gas cooler), throttling means (throttling means) and vaporizer (evaporator) connect in regular turn, and the high pressure side is a supercritical pressure.In addition, the present invention also is relevant a kind of cryogen circuit device that uses the multistage compression type compressor.
Background technique
Known this kind compressor connects into ring-type with pipe arrangement in regular turn with rotary compressor (compressor), gas cooler, throttling means (expansion valve etc.) and vaporizer etc., constitutes refrigerant circulation circuit.Refrigerant gas is drawn into the low pressure chamber side of cylinder (cylinder) from the inhalation port of the rotation compression assembly of rotary compressor, and compresses by the action of roller and valve, to become the refrigerant gas of High Temperature High Pressure.Afterwards, from the hyperbaric chamber side,, be discharged to gas cooler through discharging the port, discharging the anechoic chamber.After the heat release of gas cooler place,, be supplied to vaporizer again at refrigerant gas with the throttling in addition of throttling means.Refrigerant is in the evaporation of vaporizer place, and bring into play cooling action by heat absorption around it this moment.
In recent years, in order to handle the earth environment problem, in this refrigerant cycle loop, also use the carbon dioxide (CO of nature refrigerant 2), and do not use traditional freon (freon), and develop in the high pressure side device that turns round with supercritical pressure and use the conversion critical refrigerant circulation circuit.
In this kind conversion critical refrigerant circulation circuit, compress in order to prevent liquid refrigerant from getting back to compressor, just install absorption cell (receiver tank) in the outlet side and the low voltage side between the compressor suction side of vaporizer.Liquid refrigerant can be piled up absorption cell, only has gas can be inhaled into compressor.Adjust the throttling means, make that the refrigerant in the absorption cell can not got back to compressor (for example, Ri Ben spy opens flat 7-18602 communique).
Yet, in the low voltage side of refrigerant circulation circuit receiving groove is set and just needs abundant refrigerant charging quantity.In addition, in order to prevent liquid return, the aperture of throttling means (aperture) must be dwindled, or must enlarge the capacity of absorption cell, but this can cause cooling capacity to reduce and be provided with the problem of space enlargement.So for the problem that the liquid state that can solve compressor not installing this absorption cell is compressed, this case claimant just attempts developing known refrigerant circulation circuit shown in Figure 180.
As shown in figure 18, label 10 expression bosom die mould multistage (2 sections) compression type rotary compressors (internal intermediate pressure multi-stage (two stages) rotarycompressor), its in seal container 12, the first rotation compression assembly 32 and second formation of rotating compression assembly 34 that have electric assembly (driven unit) 14 and driven by the running shaft 16 of this electric assembly 14.
The action of this refrigerant cycle device then is described.Pressure condition in the middle of the refrigerant that is sucked from the refrigerant ingress pipe 94 of compressor 10 is compressed into by the first rotation compression assembly 32 is discharged in the seal container 12 again.Afterwards, come out, flow into intermediate cooling loop 150A from refrigerant ingress pipe 92.Intermediate cooling loop 150A is arranged to make it by gas cooler 154, and in this with the heat release of air cooling mode.Middle refrigerant of pressing is just seized heat by gas cooler at this.
Afterwards, be inhaled into the second rotation compression assembly 34, carry out second section compression, and become the refrigerant gas of High Temperature High Pressure, be discharged into the outside from refrigerant discharge tube 96 again.At this moment, refrigerant is compressed to till the suitable supercritical pressure.
The refrigerant gas of discharging from refrigerant discharge tube 96 flow into gas cooler 154, and sentence the mode heat release of air cooling in this, the low voltage side refrigerant that is more come out by vaporizer 157 in this place by inner heat exchanger 160. refrigerant is again taken heat by force afterwards, and further be cooled. afterwards, refrigerant is in expansion valve 156 decompressions, and refrigerant becomes the mixed state of gas/liquid in this process, then inflow evaporator 157 evaporations again. the refrigerant that comes out from vaporizer 157 is just by inner heat exchanger 160, and captures heat and be heated from high pressure side refrigerant in this place.
Then, the refrigerant that is added by inner heat exchanger 160 is inhaled in the first rotation compression assembly 32 of rotary compressor 10 from refrigerant ingress pipe 94, and repeatedly carries out above-mentioned circulation.
As mentioned above, in the conversion critical cooling circulation device of Figure 18, the refrigerant that comes out from vaporizer 157 is heated by high pressure side refrigerant by inner heat exchanger 160 and can get temperature (superheat degree), so the absorption cell of low voltage side can be abolished.But, and in compressor, cause and the phenomenon of liquid return can produce the danger of damage that liquid compression causes because the condition of running can produce unnecessary refrigerant.
In addition, again in this kind conversion critical refrigerant circulation circuit device, the evaporating temperature of vaporizer will be-30 ℃ to-40 ℃ low temperature range or the ultralow temperature scope below-50 ℃, can be because compression ratio will be very high can raises with the temperature of compressor 10 itself, so the very difficulty that becomes.
In addition, in No. 2507047 disclosed refrigerant circulation circuit device of Japan Patent, particularly use in the cryogen circuit device of bosom die mould multistage compression type rotary compressor, press refrigerant gas to be inhaled into the low pressure chamber side of cylinder from the inhalation port of the second rotation compression assembly in the middle of in the seal container, and the action by roller and valve, carry out second section compression, to become the refrigerant gas of High Temperature High Pressure; Then, be discharged into the outside from the hyperbaric chamber side through discharge port, discharge anechoic chamber.Enter the gas cooler heat release and after bringing into play the adding effect, come throttling, enter vaporizer again with expansion valve as the throttling means.After this place's heat absorption evaporation, be inhaled into the first rotation compression assembly again, and repeat above-mentioned circulation repeatedly.
Yet, to use in the cryogen circuit device of above-mentioned compressor, when restarting after stopping, the rotation compression assembly has the height pressure difference, and causes the deterioration of startability and cause damage.So, after stopping, making to reach equal pressure condition in the cryogen circuit early at compressor, have the operation that low voltage side is communicated with etc. the expansion valve standard-sized sheet with the high pressure side.But, in the middle of in first rotation the seal container that compression assembly compressed, press refrigerant gas, because after compressor stops, between low voltage side and high pressure side, not being communicated with, so will reach the needed time of balance pressure for a long time.
In addition, because the thermal capacity of compressor is big, it is slow that temperature descends.After compressor stopped, the compressor temperature inside can be higher than the other parts in the cryogen circuit.Moreover after compressor stopped, when the refrigerant in the compressor immerses (refrigerant liquefaction), compressor was in the moment of starting, and refrigerant can become gas suddenly, presses sharply in the middle of making to raise.Therefore, the middle pressure of refrigerant gas of pressing in the seal container can rotate the pressure height of the discharge side (high pressure side of cryogen circuit) of compression assembly than second on the contrary, produces so-called pressure reversal phenomenon (pressure inversionphenomenon).In this situation, the pressure behavior during compressor start is illustrated with Figure 19 and Figure 20.Pressure behavior when Figure 19 is known normal starting.Before restarting, the pressure in the cryogen circuit device reaches state of equilibrium, so compressor can be as usual starting, and presses in the middle of can not producing and the pressure of high pressure reverses.
Pressure behavior when on the other hand, Figure 20 is the generation of pressure reverse phenomenon.As shown in figure 20, at compressor 10 prestarts, low pressure and high pressure are for all pressing (solid line).But as previously mentioned, the middle pressure can be than this pressure also high (dotted line).Behind the starting compressor, middle pressure can more rise and become the same or higher pressure with high pressure phase.
Particularly, in rotary compressor, the valve of the second rotation compression assembly is for paying gesture (elastic reaction) to wheels side, so the pressure of the discharge side of the second rotation compression assembly is as the back pressure effect. still, in this situation, the discharge side pressure (high pressure) of the second rotation compression assembly is identical with the second rotation compression assembly (the middle pressure), or second rotation compression assembly (middle press) higher, so the back pressure of valve pair roller side does not have effect, the valve of the second rotation compression assembly can fly away. therefore, the second rotation compression assembly can not compress, and substantially has only the first rotation compression assembly compressing.
In addition, the valve of the first rotation compression assembly can be paid gesture in wheels side with this valve, so middle pressure the in the seal container is as the back pressure effect.But, as above-mentioned, the words that pressure in the seal container uprises, the pressure in the cylinder of the first rotation compression assembly and the missionary society of the pressure in the seal container are too big, the power that stresses on roller also can be higher than required power, cause having significant face pressure can put on sliding parts between valve front end and the roller outer circumferential face, valve and roller can produce friction, and the danger of damage is arranged.
On the other hand, as previously mentioned, in the middle of by the compression of first rotary compressor, press refrigerant when intermediate heat exchanger cools off, can be had the situation that can't satisfy desired temperature by the high pressure refrigerant gas of the second rotation compression assembly compression according to operational situation.
Particularly, when compressor start, the temperature of refrigerant is difficult to rise.In addition, also have refrigerant gas and immerse the interior situation generation (liquefaction) of compressor.When this situation, the temperature in the compressor is risen early to be returned to normal operation.But, as previously mentioned, to be cooled off at intermediate heat exchanger by the refrigerant of first rotary compressor compression, when making it be drawn into second rotary compressor, it is very difficult that the compressor temperature inside is risen early.
In addition, in above-mentioned compressor, the last side opening of the cylinder of the second rotation compression assembly is covered by upper support portion material, and open lower side is then covered by the intermediate section dividing plate.On the other hand, roller is arranged in the interior cylinder of the second rotation compression assembly.The eccentric part of this roller and running shaft is chimeric.For design problem or prevent the friction of roller, have plurality of gaps to be formed to be configured in the aforementioned supporting portion material of roller and roller upside and be configured in roller and the intermediate section dividing plate of roller downside between.Therefore, can be flow into roller inboard (space of the eccentric part periphery of roller inboard) from this gap by the high pressure refrigerant gas of the cylinder compresses of the second rotation compression assembly.Thus, high-pressure refrigerant can reside in the roller inboard.
As mentioned above, if high-pressure refrigerant resides in the words of roller inboard, because the pressure of roller inboard can be higher than the interior pressure (the middle pressure) of seal container that the bottom becomes accumulator, so through the oilhole in the running shaft, utilize pressure difference that oil is supplied to the roller inboard and can become very difficult.The fuel feeding quantitative change meeting of the eccentric part periphery of pair roller inboard produces not enough phenomenon.In known technology, shown in the 21st figure, path 200 is formed on the upper support portion material 201 of the cylinder upside that is configured in the second rotation compression assembly, in the roller inboard (eccentric part side) and seal container that are communicated with the second rotation compression assembly.The high pressure refrigerant gas that resides in the roller inboard can be discharged in the seal container, becomes high pressure conditions to prevent the roller inboard.
Yet, be communicated with the inboard and seal container inside of roller in order to form above-mentioned path 200, must form opening in wheels side in the inner margin portion of upper support portion material 201.That is two paths of the path 200A that will be processed to form axis direction and the substantially horizontal path 200B that is used for being communicated with this path 200A and seal container inside.In order to form path, the processing operation must increase, and then causes the surging problem of cost of production.
On the other hand, for the second rotation compression assembly, because the pressure (high pressure) in the cylinder of the second rotation compression assembly can be higher than the bottom as the pressure in the seal container of accumulator (the middle pressure), oilhole or oil supply hole from running shaft, utilize pressure difference to supply oil to the difficulty that to become very in the cylinder of the second rotation compression assembly, so only lubricate the problem that change has the fuel delivery deficiency to dissolve in the oil that sucks refrigerant.
In addition, in above-mentioned compressor, can directly be discharged into the outside by the refrigerant gas of the second rotation compression assembly compression.But, in this refrigerant gas, can sneak into the aforesaid oil that is fed to the slide part in the second rotation compression assembly, so oil is also along with refrigerant is discharged into the outside together.Therefore, the oil mass of the accumulator in the seal container can be not enough, and make the greasy property of slide part become deterioration.In addition, in the cryogen circuit of freeze cycle, also there is volume oil to flow out, and makes the freeze cycle mis-behave.In addition, for anti-problem here, if minimizing to the oily supply of second rotary compressor, then can cause the cyclicity of the slide part of the second rotation compression assembly to have problems.
Summary of the invention
Therefore, the objective of the invention is to propose a kind of refrigerant circulation circuit, its high pressure side becomes supercritical pressure, does not need to be provided with receiving groove, can prevent that just compressor is because of damage that liquid compression caused.
Another object of the present invention is to propose a kind of cooling circulation device, does not need to be provided with receiving groove in low voltage side, just can prevent compressor because of the damage that liquid compression caused, and cooling capacity is promoted.
Another object of the present invention is to propose a kind of cooling circulation device that uses the multistage compression type compressor, the phenomenon that can avoid pressure to reverse, and the startability and the durability of lifting compressor.
Another object of the present invention is to propose a kind of cooling circulation device that uses the multistage compression type compressor, can prevent overheat of compressor and the discharge temperature of the refrigerant guaranteeing to be discharged by the second rotation compression assembly compression.
Another object of the present invention is to propose a kind of cooling circulation device that uses the multistage compression type compressor, avoid the roller inboard to become the shortcoming of high pressure with better simply structure, and can positively and smoothly oil be supplied with in the cylinder of the second rotation compression assembly.
Another object of the present invention is to propose a kind of rotary compressor, and it can not reduce the fuel delivery to the rotation compression assembly, and can do one's utmost to reduce the amount that oil flows out to refrigerating circuit.
For reaching above-mentioned and other purpose, the present invention proposes a kind of cooling circulation device, and wherein compressor, gas cooler, throttling means are connected in regular turn with vaporizer, and become supercritical pressure in the high pressure side.Cooling circulation device comprises with lower member.Aforementioned compressor is in seal container, have more the moving assembly of power backup and by first and second rotation compression assembly that electric assembly drove, be compressed sucking in the second rotation compression assembly by the first rotation compression assembly compression and the refrigerant of discharging, and be discharged in the gas cooler.Intermediate cooling loop makes the refrigerant of discharging from the first rotation compression assembly, in the gas cooler heat release.First inner heat exchanger makes from gas cooler to come out and carry out heat exchange from the second rotation refrigerant of compression assembly and the refrigerant that vaporizer comes out.Second inner heat exchanger gas cooler is come out and the intermediate cooling loop flowing refrigerant with come out and come the refrigerant of from evaporator drier to carry out heat exchange from first inner heat exchanger.Therefore, the refrigerant that comes out from vaporizer carries out heat exchange at the refrigerant that flows through intermediate cooling loop that first inner heat exchanger and gas cooler come out, to capture heat.Therefore, the degree of superheat of refrigerant can be positively kept, and liquid compression can be avoided at compressor.
On the other hand, gas cooler come out from the refrigerant of the second rotation compression assembly at first inner heat exchanger, capture heat from the refrigerant that vaporizer comes out, with this refrigerant temperature is descended.In addition, because possess intermediate cooling loop, so the compressor temperature inside can descend.Particularly in this situation, the refrigerant that flows through intermediate cooling loop gives the refrigerant of from evaporator drier with heat, in being inhaled into the second rotation compression assembly after the gas cooler heat release.Therefore, can not produce because of the compressor inside temperature rising that second inner heat exchanger produces is set.
In above-mentioned cooling circulation device, because refrigerant uses carbon dioxide, so environmental problem is contributed to some extent.
In above-mentioned cooling circulation device, the evaporating temperature of the refrigerant of vaporizer is very effective at+12 ℃ to-10 ℃.
The present invention more proposes a kind of cooling circulation device, compressor wherein, gas cooler, the throttling means are connected in regular turn with vaporizer, and become supercritical pressure in the high pressure side. and cooling circulation device comprises with lower member. aforementioned compressor is in seal container, have more the moving assembly of power backup and by first and second rotation compression assembly that electric assembly drove, be compressed to suck in the second rotation compression assembly by the refrigerant of the first rotation compression assembly compression and discharge, and being discharged in the gas cooler. intermediate cooling loop makes the refrigerant of discharging from the first rotation compression assembly, in the gas cooler heat release. oil content is from means, in order to oil from being separated the refrigerant of the second rotation compression assembly. oil circuit will be separated the oil decompression that means separate by oil, oil is got back in the compressor. first inner heat exchanger makes from gas cooler to come out and carry out heat exchange from refrigerant and the refrigerant that vaporizer comes out of the second rotation compression assembly. and second inner heat exchanger makes the oil that flows at oil circuit and comes out and come the refrigerant of from evaporator drier to carry out heat exchange from first inner heat exchanger. and the throttling means are made of first throttle means and the second throttling means in first throttle means downstream side. the part refrigerant of injection loop in order to will between first and second throttling means, flowing, be injected into the suction side of the second rotation compression assembly of compressor. therefore, the refrigerant that comes out from vaporizer carries out heat exchange to capture heat at the refrigerant that flows through intermediate cooling loop that first inner heat exchanger and gas cooler come out, and carry out heat exchange at second inner heat exchanger and the oil that flows through oil circuit, to capture heat. therefore, the degree of superheat of refrigerant can be positively kept, and liquid compression can be avoided at compressor.
On the other hand, gas cooler come out from the refrigerant of the second rotation compression assembly at first inner heat exchanger, captured heat by the refrigerant that vaporizer comes out, with this refrigerant temperature is descended.In addition, because possess intermediate cooling loop, so the compressor temperature inside can descend.
In addition, the oil that flows through oil circuit returns in the compressor after the refrigerant that comes from evaporator drier that second inner heat exchanger is come out by first inner heat exchanger is captured heat, so the compressor temperature inside can further reduce.
Moreover because flow through part refrigerant between first and second throttling means, the suction side of the second rotation compression assembly by being injected into compressor behind the injection loop again is so utilize the refrigerant of this injection can cool off the second rotation compression assembly.Thus, the compression efficiency of the second rotation compression assembly can be improved, and the temperature of compressor itself also can further descend.Therefore, in the refrigerant cycle, the refrigerant evaporating temperature at vaporizer is descended.
In aforesaid cooling circulation device, more comprise the gas-liquid separation means being set between first and second throttling means.Injection loop will be reduced pressure by the liquid refrigerant that the gas-liquid separation means are separated, and is re-introduced into the suction side of the second rotation compression assembly of compressor.Therefore, utilize the heat-absorbing action along with the evaporation of injecting refrigerant, second rotary compressor can more effectively be cooled.Thus, in the refrigerant cycle, the refrigerant evaporating temperature at vaporizer is descended.
In aforesaid cooling circulation device, oil circuit makes to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place and carries out heat exchange, returns in the seal container of compressor.Therefore, utilize this oil can reduce the interior temperature of seal container of compressor effectively.
In aforesaid cooling circulation device, oil circuit is to make to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place to carry out heat exchange, returns second this suction side that rotates compression assembly of compressor.Therefore, can lubricate the second rotation compression assembly on one side improving compression efficiency, and can reduce the temperature of compressor itself effectively.
It is the R23 of refrigerant, any refrigerant in the nitrogen oxide that refrigerant in the aforementioned cooling circulation device can use carbon dioxide, HCF, so environmental problem is contributed to some extent.
In addition, in above-mentioned cooling circulation device, the evaporating temperature of the refrigerant of vaporizer is very effective below-50 ℃.
The present invention more proposes a kind of cooling circulation device, compressor wherein, gas cooler, the throttling means are connected in regular turn with vaporizer, and become supercritical pressure in the high pressure side. and cooling circulation device comprises with lower member. aforementioned compressor is in seal container, have more the moving assembly of power backup and by first and second rotation compression assembly that electric assembly drove, be compressed to suck in the second rotation compression assembly by the refrigerant of the first rotation compression assembly compression and discharge, and being discharged in the gas cooler. intermediate cooling loop makes the refrigerant of discharging from the first rotation compression assembly, in the gas cooler heat release. first inner heat exchanger makes from gas cooler to come out and carry out heat exchange from the refrigerant of the second rotation compression assembly with the refrigerant that vaporizer comes out. oil content from means in order to oil is separated from by the refrigerant of the second rotation compression assembly. oil circuit will be separated the oil that means separate by oil and reduce pressure, oil is got back in the compressor. second inner heat exchanger makes the oil that flows at oil circuit and comes out from first inner heat exchanger and come the refrigerant of from evaporator drier to carry out heat exchange. therefore, the refrigerant that comes out from vaporizer carries out heat exchange to capture heat at the refrigerant that flows through intermediate cooling loop that first inner heat exchanger and gas cooler come out, and carry out heat exchange at second inner heat exchanger and the oil that flows through oil circuit, to capture heat. therefore, the degree of superheat of refrigerant can be positively kept, and liquid compression can be avoided at compressor.
On the other hand, gas cooler come out from the refrigerant of the second rotation compression assembly at first inner heat exchanger, captured heat by the refrigerant that vaporizer comes out, with this refrigerant temperature is descended.In addition, because possess intermediate cooling loop, so the compressor temperature inside can descend.
In addition, the oil that flows through oil circuit returns in the compressor after the refrigerant that comes from evaporator drier that second inner heat exchanger is come out by first inner heat exchanger is captured heat, so the compressor temperature inside can further reduce.Thus, the refrigerant temperature of the vaporizer in the refrigerant cycle can be lowered.
In aforesaid cooling circulation device, oil circuit is to make to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place to carry out heat exchange, returns in the seal container of compressor.Therefore, utilize this oil can reduce the interior temperature of seal container of compressor effectively.
In aforesaid cooling circulation device, oil circuit makes to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place and carries out heat exchange, returns second this suction side that rotates compression assembly of compressor.Therefore, can lubricate the second rotation compression assembly on one side improving compression efficiency, and can reduce the temperature of compressor itself effectively.
In above-mentioned cooling circulation device, because refrigerant uses carbon dioxide, so environmental problem is contributed to some extent.
In above-mentioned cooling circulation device, the evaporating temperature of the refrigerant of vaporizer is very effective at-30 ℃ to-40 ℃.
The present invention more proposes a kind of cooling circulation device.Compressor possesses and is driven first and second rotation compression assembly that assembly drives.Be compressed sucking in this second rotation compression assembly by the first rotation compression assembly compression and the refrigerant of discharging, and be discharged in this gas cooler.Bypass circulation under the refrigerant decompression that will not discharge from the first rotation compression assembly of compressor, supplies to vaporizer to refrigerant; And control valve unit, in order to when the evaporator defrost, open this bypass circulation.Control valve unit is also opened the stream of this bypass circulation when this compressor start.Therefore, when vaporizer defrosts, open control valve unit, the refrigerant of discharging from first compression assembly flows through bypass circulation, under not reducing pressure, supplies with the vaporizer heating.
In addition, when compressor start, control valve unit is also open, and through bypass circulation, the discharge side of first compression assembly, that is the pressure of second compression assembly suction side can be run away to vaporizer.The phenomenon that the pressure of the discharge side (high pressure) of the suction side of the second rotation compression assembly in the time of therefore, can avoiding compressor start (the middle pressure) and second compression assembly reverses.
In above-mentioned cooling circulation device, control valve unit from before the compressor start to a scheduled time, open bypass circulation.
In addition, this control valve unit also can be from compressor start in a scheduled time, open bypass circulation.
Perhaps, this control valve unit can from after this compressor start to a scheduled time, open bypass circulation.
The present invention more proposes a kind of cooling circulation device, wherein compressor, gas cooler, throttling means are connected in regular turn with vaporizer. and compressor possesses first and second rotation compression assembly, be compressed to suck in the second rotation compression assembly by the refrigerant of the first rotation compression assembly compression and discharge, and being discharged in the gas cooler. cooling circulation device comprises: the refrigerant pipe arrangement is used for making by the refrigerant of the first rotation compression assembly compression being inhaled into the second rotation compression assembly; Intermediate cooling loop is connected side by side with cold pipe arrangement; And control valve unit, make the cryogen flow of discharging from first rotary compressing device to refrigerant pipe arrangement or intermediate cooling loop in order to control. therefore, can select whether to flow into intermediate cooling loop according to the state of refrigerant.
The detecting of refrigerant state is to utilize pressure or temperature to carry out.That is when the second rotation discharge refrigerant pressure of compression assembly or refrigerant temperature rose to predetermined value, control valve unit made refrigerant flow through intermediate cooling loop, and when being lower than predetermined value, refrigerant flows through the refrigerant pipe arrangement.
Above-mentioned cooling circulation device more can comprise temperature detect means, is used for detecting the refrigerant temperature of discharging from the second rotation compression assembly.The discharge refrigerant temperature of the second rotation compression assembly that detects when temperature detect means is when rising to a predetermined value, and control valve unit makes cryogen flow arrive intermediate cooling loop.When lower, make cryogen flow arrive the refrigerant pipe arrangement than predetermined value.
The present invention more proposes a kind of compressor, has first and second rotation compression assembly that running shaft drove that is driven assembly at seal container.Be discharged in this seal container by the first rotation refrigerant that compression assembly compressed, press refrigerant gas in the middle of giving off again by the second rotation compression assembly compression.Compressor comprises following formation: two cylinders constitute first and second rotation compression assembly respectively; Two rollers are separately positioned in each cylinder, and are chimeric and do eccentric rotation with the eccentric part of running shaft; Intermediate section dividing plate, position are between each cylinder and each roller, to cut apart first and second rotation compression assembly; Two supporting portion materials are sealed the respectively opening surface of this cylinder respectively, and respectively possess the bearing of this running shaft; Oilhole is formed in the running shaft; Through hole, perforation is arranged in the intermediate section dividing plate, to be communicated with the inboard of seal container inside and two rollers; Inject and use intercommunicating pore, perforation is arranged in the cylinder of the second rotation compression assembly, in order to the through hole and second suction side that rotates compression assembly that is communicated with the intermediate section dividing plate; And intercommunicating pore, extend and pass this intermediate section dividing plate at the upside midway of this through hole.The through hole of intermediate section dividing plate thus, the high-pressure refrigerant that is accumulated in the roller inboard can be run away in the seal container.
In addition, even the pressure in the cylinder of the second rotation compression assembly is higher than the pressure that becomes in the middle seal container of pressing, utilization is at the suction crushing of the suction process of the second rotation compression assembly, by the through hole and the intercommunicating pore of intermediate section dividing plate, oil can positively supply to the suction side of the second rotation compression assembly from the oilhole of running shaft.Because the through hole of intermediate section dividing plate can reach that the high pressure of double as roller inboard discharges and to the fuel feeding of the second rotation compression assembly, so can reach the purpose that structure is simplified and cost reduces.
Driven unit in the aforesaid compressor is the revolution control type motor that starts with low speed when starting.When starting, though the second rotation compression assembly from seal container in the through hole of the intermediate section dividing plate that is communicated with suck oil the seal container, also can suppress because the bad influence that oil pressure contracts and caused, also can avoid the reliability decrease of rotary compressor.
The present invention more proposes a kind of compressor.In seal container, possess electric assembly with by rotation compression assembly that electric assembly drove.Be rotated the refrigerant that compression assembly compresses and be discharged into the outside, compressor forms reservoir in the rotation compression assembly, in order to being separated, be accumulated with the oil that refrigerant emits from the rotation compression assembly, and reservoir is communicated to seal container inside via the return path with throttling function.Therefore, the oil mass that is discharged into the rotary compressor outside from the second rotation compression assembly can reduce.
The present invention more proposes a kind of compressor.In seal container, has electric assembly and by rotary compressor structure that electric assembly drove.The rotary compressor structure is made of first and second rotation compression assembly, is discharged in the seal container by the first rotation refrigerant that compression assembly compressed, and presses refrigerant to compress with the second rotation compression assembly in the middle of emitting, and is discharged into the outside.Compressor forms reservoir in the rotary compressor structure, be separated, accumulate with the oil that refrigerant emits in order to rotating compression assembly from second, and reservoir is communicated to seal container inside via the return path with throttling function.Therefore, the oil mass that is discharged into the rotary compressor outside from the second rotation compression assembly can reduce.
Above-mentioned compressor more comprises: second cylinder constitutes the second rotation compression assembly; First cylinder sees through the intermediate section dividing plate and is configured in second cylinder below, and in order to constitute the first rotation compression assembly; The first supporting portion material is in order to seal the below of first cylinder; The second supporting portion material is in order to seal the top of second cylinder; And the suction path, in the first rotation compression assembly.Reservoir is formed in first cylinder that sucks part beyond the path.Constitute thus, space efficiency is promoted.
In the above-mentioned compressor, reservoir utilizes up/down perforation second cylinder, intermediate section dividing plate, constitutes with the through hole of first cylinder.Therefore, can improve the processing operation that constitutes reservoir significantly.
Description of drawings
Fig. 1 illustrates the sectional arrangement drawing of the bosom die mould multistage compression type rotary compressor that constitutes conversion critical refrigerant circulation circuit of the present invention.
Fig. 2 is according to the cryogen circuit figure of the conversion critical cooling circulation device that the embodiment of the invention illustrated.
Fig. 3 illustrates the p-h line chart of the cryogen circuit of Fig. 2.
Fig. 4 is according to the cryogen circuit figure of the conversion critical cooling circulation device that another embodiment of the present invention illustrated.
Fig. 5 is according to the cryogen circuit figure of the conversion critical cooling circulation device that another embodiment of the present invention illustrated.
Fig. 6 is according to the cryogen circuit figure of the conversion critical cooling circulation device that another embodiment of the present invention illustrated.
Fig. 7 is according to the cryogen circuit figure of the conversion critical cooling circulation device that another embodiment of the present invention illustrated.
Fig. 8 illustrates the cryogen circuit figure of cooling circulation device.
Pressure behavior figure when Fig. 9 illustrates the compressor start of cryogen circuit device of the present invention.
Figure 10 illustrates the pressure behavior figure of corresponding diagram 9 among another embodiment.
Figure 11 illustrates the cryogen circuit figure of cooling circulation device.
Figure 12 illustrates when the discharge refrigerant temperature of the second rotation compression assembly rises to predetermined value, the p-h line chart of cryogen circuit.
Figure 13 illustrates the planimetric map of intermediate section dividing plate of the rotary compressor of Fig. 1.
Figure 14 illustrates the sectional arrangement drawing of intermediate section dividing plate of the rotary compressor of Fig. 1.
Figure 15 illustrates the through hole of intermediate section dividing plate of the rotary compressor that is formed at Fig. 1 at the enlarged view of seal container side.
Figure 16 illustrates the pressure oscillation figure of casing top half suction side of the rotary compressor of Fig. 1.
Figure 17 illustrates the sectional arrangement drawing of the bosom die mould multistage compression type rotary compressor of another embodiment of the present invention.
Figure 18 illustrates the cryogen circuit figure of known cooling circulation device.
Pressure behavior figure when Figure 19 illustrates the compressor normal starting of known cryogen circuit device.
Figure 20 illustrates the pressure behavior figure that known generation pressure reverses phenomenon.
The 21st figure illustrates the sectional arrangement drawing of the upper support portion material of known rotary compressor.
The reference numerals explanation
10 compressors, 12 seal containers
12A vessel 12B lid
12C accumulator 12D mounting hole
14 electric assemblies, 16 running shafts
18 rotary compressor structures
20 terminals, 22 stators
24 rotors, 26 laminated members
28 stator coils, 30 laminated members
32 first rotation compression assemblies, 34 second rotation compression assemblies
36 intermediate section dividing plates
40 times cylinders of 38 casing top halfs
42, eccentric part supporting portion material about in the of 54,56 about in the of 44
54A, 56A bearing 58,60 suck path
62,64 discharge anechoic chamber's 66,68 loam cake and lower covers
78 main screw 80 drain passageways
82,84 transverse direction oil supply holes, 92 refrigerant ingress pipes
94 refrigerant ingress pipes, 96 refrigerant discharge tube
100 reservoirs, 110 return paths
102 oil pumps, 103 restriction materials
Discharge tube 129 main screws in the middle of 121
131 through holes, 133,134 intercommunicating pores
141,142,143,144 bushing pipes
150 intermediate cooling loop 152A intermediate cooling loops
156 expansion valves
First and second expansion valve of 156A, 156B
157 vaporizers, 152,158 solenoid valves
160,162 first and second inner heat exchangers
161 suck port 170 oil separators
175,175A oil circuit 176 capillary tubies
180 bypass circulations
190 effluent air temp sensors
200 gas-liquid separators, 210 injection loops
220 capillary tubies
Embodiment
For above-mentioned purpose of the present invention, feature and advantage can be become apparent, preferred embodiment cited below particularly, and conjunction with figs. are described in detail below:
Then describing embodiments of the invention Fig. 1 with reference to the accompanying drawings in detail is cooling circulation device of the present invention, particularly come as embodiment with the compressor that is used in the conversion critical cooling circulation device, and for possessing the sectional arrangement drawing that first and second rotates bosom die mould multistage (2 sections) compression type rotary compressor 10 of compression assembly 32,34.Fig. 2 is the cryogen circuit figure of conversion critical cooling circulation device of the present invention.In addition, conversion critical cooling circulation device of the present invention is used in vending machine, air conditioner or freezer, show cabinet etc.
In each was graphic, label 10 was with carbon dioxide (CO 2) the bosom die mould multistage compression type rotary compressor that uses for refrigerant. compressor 10 is by cylindric seal container 12 that steel plate constituted; Configuration is accommodated in the electric assembly 14 of the upside of these seal container 12 inner spaces; And be configured in electric assembly 14 downsides, with electric assembly 14 running shaft 16 was driven first changes the institutes such as rotary compressor structure 18 that compression assembly (first section) 32 and second rotates compression assembly (second section) 34 etc. and constitute. in addition, the volume of the first rotation compression assembly 32 of the rotary compressor 10 of present embodiment can for example be 2.89cc, can for example be 1.88cc then as second section second volume that rotates compression assembly 34
The bottom of seal container 12 is as accumulator, and by electric assembly 14, take in rotary compressor structure 18 vessel 12A, be used for covering the upper opening of vessel 12A and slightly become bowl-shape institutes such as lid 12B to constitute.In addition, Yuan Xing mounting hole 12D is formed at the center above the lid 12B.Supply electric power is installed among this mounting hole 12D for 20 of the terminals (omission distribution) of electric assembly 14.
Electric assembly 14 is the centralized DC motor of so-called magnetic pole, comprises along the inner peripheral surface of seal container 12 upper spaces and the stator of installing with ring-type 22, to insert the rotor 24 that is arranged at stator 22 inboards slightly at interval.Rotor 24 is fixed on the running shaft 16 of signing the direction extension of hanging down by the center.Stator 22 has the laminated member 26 that forms with ring-type (doughnut shape) electromagnetic steel plate storehouse, and rolls up in the mode of laminated member 26 tooth portions and the stator coil 28 that is rolled into straight.In addition, rotor 24 is identical with stator 22, also is that the laminated member 30 with electromagnetic steel plate is formed, and inserts permanent magnet MG constitute rotor 24 in laminated member 30.
In addition, as the oil pump 102 of fuel feeding means in running shaft 16 underparts.Utilize this oil pump 102, the oil of lubricated usefulness just can be drunk up from the accumulator that constitutes seal container 12 bottoms, through vertical direction is formed at running shaft 16 in spool in oilhole (not drawing) in the heart, from the transverse direction oil supply hole 82,84 that is communicated with oilhole (formation also being arranged at eccentric part 42,44 up and down), oil just is supplied to the slide part of eccentric part 42,44 up and down and first and second rotation compression assembly 32,34 etc.Thus, just can prevent the abrasion of first and second rotation compression assembly 32,34.
Intermediate section dividing plate 36 is seized on both sides by the arms between the first rotation compression assembly 32 and the second rotation compression assembly 34.That is the first rotation compression assembly 32 and the second rotation compression assembly 34 are by intermediate section dividing plate 36; Casing top half 38 and following cylinder 40 are configured on intermediate section dividing plate 36 upper-lower positions; Last bottom roller 46,48 has the phase difference of 180 degree and is doing eccentric rotation in the cylinder 38,40 up and down by the eccentric part up and down 42,44 that is arranged on the running shaft 16; Valve contacts with last bottom roller 46,48, is divided into low pressure chamber side and hyperbaric chamber side respectively in the cylinder 38,40 up and down; And upper support portion material 54 and lower support portion material 56 be in order to sealing casing top half 38 upside opening surfaces and following cylinder 40 open lower side faces, and doublely make the bearing of running shaft 16 and as the supporting portion material.
On the other hand, the discharge anechoic chamber 62,64 of suction path 58,60 and depression is formed in upper support portion material 54 and the lower support portion material 56.Suck path 58,60 and be connected to cylinder 38,40 up and down to suck port 161,161 respectively, and two opening portions of discharging the indivedual of anechoic chambers 62,64 and each cylinder 38,40 opposition side respectively the tegmentum body seal.That is, discharge anechoic chamber 62 and got up as loam cake 66 envelopes of lid, got up as lower cover 68 envelopes of lid and discharge anechoic chamber 66.
In this situation, the upright central authorities that are located at upper support portion material 54 of bearing 54A.In addition, bearing 56A breakthrough form is formed in the central authorities of lower support portion material 56.Running shaft 16 is kept by the bearing 56A of the bearing 54A of upper support portion material 54 and lower support portion material 56.
Lower cover 68 is made of the circular steel plate of round (doughnut), and four places of outer part then utilize main screw 129 to be fixed on the lower support portion material 56 from the below.The front end of main screw 129 then is bolted on the upper support portion material 54.
Discharge anechoic chamber 64 and the seal container 12 of the first rotation compression assembly 32 is interior to be communicated with access.This access is a hole of not drawing, and connects lower support portion material 56, upper support portion material 54, loam cake 66, casing top half 38, following cylinder 40 and intermediate section dividing plate 36.In this situation, the middle discharge tube 121 upright upper ends of being located at access, the then from then on middle discharge tube 121 of middle refrigerant of pressing is discharged in the seal container 12.
In addition, loam cake 66 zonings go out to discharge anechoic chamber 62, and its discharge portion not draw is connected to second casing top half 38 inside that rotate compression assembly 34.To have predetermined interval with loam cake 66, electric assembly 14 is arranged at loam cake 66 upsides.Loam cake 66 is made of the circular steel plate that slightly becomes round, tangible pore-forming on it, and this hole is for connecting the bearing 54A of upper support portion material 54.The periphery of loam cake 66 utilizes four main screws 78, is fixed on the lower support portion material 56 from the below.The front end of main screw 78 then is bolted on the lower support portion material 56.
Consideration is to influence, combustibility and the toxicity etc. of earth environment, and refrigerant uses the carbon dioxide (CO of nature refrigerant 2), the oil product that lubricant oil then for example uses mineral oil, alkylbenzene oil (alkyl benzene), ester oil (ester oil), PAG oil (poly alkyl glycol, poly-alkyl glycol) etc. both to deposit.
At the suction path 60 (upside is not drawn) of corresponding upper support portion material 54 and lower support portion material 56, discharge on the position of anechoic chamber 62, loam cake 66 upsides (position of the lower end of rough corresponding electric assembly 14), bushing pipe 141,142,143,144 welds respectively on the side of the vessel 12A that is fixed in seal container 12.An end that refrigerant is imported the refrigerant ingress pipe 92 of casing top half 38 inserts and is connected in the bushing pipe 141, and an end of this refrigerant ingress pipe 92 then is communicated in the absorption path (not drawing) of casing top half 38.Refrigerant ingress pipe 92 arrives bushing pipes 144 through second inner heat exchanger 162, gas cooler 154 backs that are arranged on the intermediate cooling loop 150 described later, and the other end then inserts and is connected in the bushing pipe 144 and is communicated in the seal container 12.Or refrigerant ingress pipe 92 is via there being the intermediate cooling loop 150 by gas cooler 154 described later to arrive bushing pipe 144, and the other end then inserts and is connected in the bushing pipe 144 and is communicated in the seal container 12.
Second inner heat exchanger 162 be for gas cooler 154 and flow through intermediate cooling loop 150 in the middle of press refrigerant and for first inner heat exchanger 160 and come to carry out heat exchange between the low voltage side refrigerant of from evaporator drier 157.Or second inner heat exchanger 162 is at the oil that flows through oil circuit 175 and for first inner heat exchanger 160 and carry out heat exchange between the low voltage side refrigerant of from evaporator drier 157.
In addition, the end insertion of the refrigerant ingress pipe 94 of cylinder 40 is connected in the bushing pipe 142 to be used for importing refrigerant down, and an end of this refrigerant ingress pipe 94 then is communicated to down the suction path 60 of cylinder 40.The other end of refrigerant ingress pipe 94 then is connected to second inner heat exchanger.In addition, refrigerant discharge tube 96 is inserted and is connected in the bushing pipe 143, and an end of this refrigerant discharge tube 96 is connected to discharge anechoic chamber 62.
Second embodiment
Then with reference to figure 2, above-mentioned compressor 10 is the part of the cryogen circuit of pie graph 2.That is the refrigerant discharge tube 96 of compressor 10 is connected to the inlet of gas cooler 154.The pipe arrangement that gas cooler 154 comes out is then by aforesaid first inner heat exchanger 160.First inner heat exchanger is to carry out heat exchange between the low voltage side refrigerant that the high pressure side refrigerant that gas cooler comes out and vaporizer 157 come out.
Refrigerant by first inner heat exchanger 160 arrives the expansion valve 156 as the throttling means.The outlet of expansion valve 156 is connected to the inlet of vaporizer 157, and the pipe arrangement that vaporizer 157 comes out arrives aforementioned second inner heat exchanger 162 then through first inner heat exchanger 160.The pipe arrangement that second inner heat exchanger 162 comes out then is connected to refrigerant ingress pipe 94.
One side is with reference to the p-h line chart (Mo Liye line chart, Mollier diagram) of figure 3, Yi Bian the action of the conversion critical cooling circulation device of the present invention of above-mentioned formation is described.Via terminal 20 and the distribution do not drawn, after stator coil 28 energisings of the electric assembly 14 of compressor 10, electric assembly 14 just starts and rotor 24 also rotates thereupon.Rotate by this, chimeric the last bottom roller 46,48 of the eccentric part up and down that is wholely set with running shaft 16 42,44 is eccentric rotation the in cylinder up and down just.
Thus, via the suction path that is formed in refrigerant ingress pipe 94 and the lower support portion material 56, the suction port of never drawing is drawn into the low-pressure refrigerant gas (state of Fig. 3 1.) of the low pressure chamber side of cylinder 40, can be by the action of roller 48 with valve, be compressed into the centre and press, again from descending the hyperbaric chamber side of cylinder 40, via the access of not drawing, be discharged in the seal container 12 from middle discharge tube 121. thus, pressure condition (state of Fig. 3 is 2.) in the middle of seal container 12 just becomes.
Then, the middle refrigerant gas of pressing in the seal container 12 enters refrigerant ingress pipe 92, comes out from bushing pipe 144 again, flows into intermediate cooling loop 150.Then, intermediate cooling loop 150 is by in the process of gas cooler 154, carries out heat release (state of Fig. 3 2. ') in the mode of air cooling, afterwards again by second inner heat exchanger 162.Refrigerant is just captured heat at this from low-pressure refrigerant, with further be cooled (state of Fig. 3 3.).
With Fig. 3 this state is described.The refrigerant gas that flows through intermediate cooling loop 150 is in gas cooler 154 places heat release, and this moment, entropy lost Δ h1.Moreover, at second inner heat exchanger 162, captured heat by low voltage side refrigerant and cool off entropy loss Δ h3.So, by making by intermediate cooling loop 150, pressed refrigerant gas to be cooled off effectively in the middle of 32 compressions of the first rotation compression assembly by the gas cooler 154 and second inner heat exchanger 162, can be suppressed so the temperature in the seal container 12 rises, and the compression efficiency of the second rotation compression assembly 34 also can promote.
Then, press refrigerant gas via the suction path (not drawing) that is formed in the upper support portion material 54 in the middle of being cooled, the suction port of never drawing is inhaled into the low pressure chamber side of the casing top half 38 of the second rotation compression assembly 34.By roller 46 action, carry out second section and compress and become the High Temperature High Pressure refrigerant gas with valve.Then, from the hyperbaric chamber side, by the discharge port of not drawing, process is formed at the discharge anechoic chamber 62 in the upper support portion material 54 again, and is discharged into the outside from refrigerant discharge tube 96.At this moment, refrigerant is compressed to suitable supercritical pressure (state of Fig. 3 4.).
The refrigerant of discharging from refrigerant discharge tube 96 flows into to gas cooler 154, and sentences air cooling mode heat release (state of Fig. 3 5. ') in this, afterwards again by first inner heat exchanger 160.Refrigerant is in being captured heat by low voltage side refrigerant herein, and further be cooled (state of Fig. 3 5.).
This state illustrates with Fig. 3.In other words, when not having first inner heat exchanger 160,5. the entropy of the refrigerant of expansion valve 156 inlet becomes ' state.In this situation, the refrigerant temperature of vaporizer 157 can uprise.On the other hand, when first inner heat exchanger 160 makes when doing heat exchange with low voltage side refrigerant, the entropy decline Δ h2 of refrigerant, and the state that becomes Fig. 3 is 5..Therefore, with the state (5) of Fig. 3 ' entropy, the refrigerant temperature of vaporizer 157 can step-down.Therefore, the cooling capacity that first inner heat exchanger 160 can promote the refrigerant gas of vaporizer 157 is set.
Therefore, also can reach desired evaporating temperature at an easy rate not increasing under the refrigerant circulation quantity, for example be+12 ℃ to-10 ℃ middle high-temperature scope in the evaporating temperature of vaporizer 157.In addition, the power consumption of compressor also can reduce.
High pressure side refrigerant gas by 160 coolings of first inner heat exchanger arrives expansion valve 156.In the ingress of expansion valve 156, refrigerant gas or gaseous state.Because the pressure of expansion valve 156 descends, refrigerant can become the mixture (state of Fig. 3 is 6.) of gas/liquid two-phase, and with in this state inflow evaporator 157.Refrigerant utilizes from the effect of air heat absorption in the evaporation of vaporizer 157 places, brings into play cooling action.
Afterwards, refrigerant flows out (state of Fig. 3 1. ") from vaporizer 157, by first inner heat exchanger 160.In this place, capture heat from high pressure side refrigerant and after being subjected to heat effect (state of Fig. 3 1. '), arrive second inner heat exchanger 162.Then, at second inner heat exchanger 162, capture heat from the middle refrigerant of pressing that flows through intermediate cooling loop 150, to be subjected to further heat effect (state of Fig. 3 1.).
With Fig. 3 this state is described. become low temperature in vaporizer 157 evaporations, and from the refrigerant that vaporizer 157 comes out be state shown in Figure 3 1. ". refrigerant is not the perfect gas state; but mixing liquid. by carrying out heat exchange; the entropy of the refrigerant Δ h2 that can rise by first inner heat exchanger 160 and high pressure side refrigerant; and the state that becomes Fig. 3 1. '. thus; refrigerant can almost completely become gas. moreover; by pressing refrigerant to carry out heat exchange in second inner heat exchanger 162 and centre, the entropy of the refrigerant Δ h3 that can rise, and the state that becomes Fig. 3 1., refrigerant can positively get temperature, and becomes gas fully.
Thus, the refrigerant that comes out from vaporizer 157 can positively be gasified.Particularly, even when under operating condition, producing residue refrigerant, utilize first inner heat exchanger 160 and second inner heat exchanger 162, heat low voltage side refrigerant with two stages, just can prevent positively that liquid refrigerant is inhaled into the liquid return phenomenon in the compressor 10 so can not need to be provided with absorption cell, and can avoid compressor 10 because the suffered damage of liquid return.
In addition as previously mentioned, come from evaporator drier 157 and by the low-pressure refrigerant of first inner heat exchanger 160 heating and pressed refrigerant to carry out heat exchange in the middle of the compression of first rotary compressor at second inner heat exchanger 162.After both sides carried out heat exchange, the hot revenue and expenditure in the compressor was zero in the compressor 10 so refrigerant is inhaled into.
Therefore, under discharge temperature that can not make compressor 10 or inside temperature rising, the degree of superheat can be guaranteed.Therefore, the reliability of conversion critical cooling circulation device can promote.
In addition, by the refrigerant of second inner heat exchanger, 162 heating, be inhaled into the first rotation compression assembly 32 of compressor 10 from refrigerant ingress pipe 94.This circulation operation repeatedly.
As mentioned above, possessing intermediate cooling loop 150, the refrigerant that the first rotation compression assembly 32 is given off is in gas cooler 154 heat releases; First inner heat exchanger 160, make that gas cooler 154 comes out from carrying out heat exchange between the refrigerant of the second rotation compression assembly 34 and the refrigerant that vaporizer 157 comes out; And second inner heat exchanger 162, carry out heat exchange between the refrigerant that comes from evaporator drier 157 that the refrigerant that flows through intermediate cooling loop 150 that gas cooler 154 comes out and first inner heat exchanger 160 are come out, the refrigerant that vaporizer 157 comes out can carry out heat exchange at the refrigerant from the second rotation compression assembly 34 that first inner heat exchanger 160 and gas cooler 154 come out capturing heat, and carries out heat exchange to capture heat at second inner heat exchanger 162 and the refrigerant that flows through intermediate cooling loop 150 that gas cooler 154 comes out.Therefore, the degree of superheat of refrigerant can positively be guaranteed, to avoid the liquid compression in the compressor 10.
On the other hand, the refrigerant from the second rotation compression assembly 34 that gas cooler 154 comes out can be captured heat by the refrigerant that vaporizer 157 comes out at first inner heat exchanger 160, so refrigerant temperature can descend thus.Therefore, the cooling capacity of the refrigerant gas of vaporizer 157 can promote.Therefore, do not increasing under the refrigerant circulation quantity, can reach desired evaporating temperature easily, and the power consumption of compressor can reduce also.
In addition, because possess intermediate cooling loop 150, compressor 10 temperature inside can descend.Particularly in this situation, because the refrigerant that flows through intermediate cooling loop 150 is after gas cooler 154 heat releases, can pass to heat come the refrigerant of from evaporator drier 157, this refrigerant is inhaled into the second rotation compression assembly 34 again, so second inner heat exchanger 162 is set the thing of compressor 10 temperature inside rising can not taken place.
In addition, in an embodiment, carbon dioxide is to be used as refrigerant, but the present invention is not limited thereto.Any in the conversion critical refrigerant cycle spendable various refrigerant all can use.
The 3rd embodiment
Follow with reference to figure 4 part of the cryogen circuit of above-mentioned compressor 10 pie graphs 4.That is the refrigerant discharge tube 96 of compressor 10 is connected to the inlet of gas cooler 154.Then, the pipe arrangement that comes out of gas cooler 154 is connected to the inlet that separates the oil separator 170 of means as oil.Oil separator 170 is used for separating the oil of discharging with by the refrigerant of the second rotation compression assembly, 34 compressions.
The refrigerant pipe arrangement that oil separator 170 comes out is used for carrying out that oil separator 170 comes out from the heat exchange between the high pressure side refrigerant of the second rotation compression assembly 34 and the low voltage side refrigerant that vaporizer 157 comes out by aforesaid first inner heat exchanger, 160. first inner heat exchangers 160.
Then, the high pressure side refrigerant by first inner heat exchanger 160 arrives the expansion mechanism 156 as the throttling means.Expansion mechanism 156 is by being constituted as the first expansion valve 156A of first throttle means and the second expansion valve 156B as the second throttling means that is arranged on the first expansion valve 156A downstream side.In addition, the aperture of the aforementioned first expansion valve 156A is adjusted to the centre that is higher than in the compressor 10 by the post-decompression refrigerant pressure of the first expansion valve 156A is pressed.
In addition, be arranged on refrigerant pipe arrangement between the first expansion valve 156A and the second expansion valve 156B as the gas-liquid separator 200 of gas liquid separation means.The refrigerant pipe arrangement that the first expansion valve 156A comes out is connected to the inlet of gas-liquid separator 200.The refrigerant pipe arrangement of the gas outlet side of gas-liquid separator 200 is connected to the inlet of the second expansion valve 156B.Then, the outlet of the second expansion valve 156B is connected to the inlet of vaporizer 157, and the refrigerant pipe arrangement that vaporizer 157 comes out arrives second inner heat exchanger 162 through first inner heat exchanger 160.The refrigerant pipe arrangement that second inner heat exchanger 162 comes out is connected to refrigerant ingress pipe 94.
On the other hand, the aforementioned oil circuits 175 that will be turned back in the compressor 10 by the oil of oil separator 170 separation are to be connected to oil separator 170.Capillary tube 176 as the decompression means is arranged on the oil circuit 175, and its oil that is used for being separated by oil separator 170 reduces pressure.Oil circuit 175 is communicated in the seal container 12 of compressor 10 through second inner heat exchanger 162.
In addition, injection loop (injection loop) 210 is connected to the liquid outlet side of gas-liquid separator 200, with so that the liquid refrigerant that is separated by gas-liquid separator 200 get back in the compressor 10.Capillary tube 220 as the decompression means is located on the injection loop 210, in order to being reduced pressure by the liquid refrigerant that gas-liquid separator 200 separates.This injection loop 210 is connected to the aforementioned refrigerant ingress pipe 92 that is communicated with the suction side of the second rotation compression assembly 34.
Via terminal 20 and the distribution do not drawn, after stator coil 28 energisings of the electric assembly 14 of compressor 10, electric assembly 14 just starts and rotor 24 also rotates thereupon.Rotate by this, chimeric the last bottom roller 46,48 of the eccentric part up and down that is wholely set with running shaft 16 42,44 is eccentric rotation the in cylinder up and down just.
Via terminal 20 and the distribution do not drawn, after stator coil 28 energisings of the electric assembly 14 of compressor 10, electric assembly 14 just starts and rotor 24 also rotates thereupon.Rotate by this, chimeric the last bottom roller 46,48 of the eccentric part up and down that is wholely set with running shaft 16 42,44 is eccentric rotation the in cylinder up and down just.
Thus, via the suction path 60 that is formed in refrigerant ingress pipe 94 and the lower support portion material 56, the suction port of never drawing is drawn into the low-pressure refrigerant gas of the low pressure chamber side of cylinder 40, can be by the action of roller 48 with valve, press in the middle of being compressed into, from the hyperbaric chamber side of following cylinder 40,, be discharged in the seal container 12 again from middle discharge tube 121 via the access of not drawing.Thus, pressure condition in the middle of seal container 12 just becomes.
By making by intermediate cooling loop 150, pressed refrigerant gas to be cooled off effectively in the middle of 32 compressions of the first rotation compression assembly by the gas cooler 154 and second inner heat exchanger 162, can be suppressed so the temperature in the seal container 12 rises, and the compression efficiency of the second rotation compression assembly 34 also can promote.
Then, press refrigerant gas via the suction port (not drawing) that is formed in the upper support portion material 54 in the middle of being cooled, the suction port of never drawing is inhaled into the low pressure chamber side of the casing top half 38 of the second rotation compression assembly 34.By roller 46 action, carry out second section and compress and become the High Temperature High Pressure refrigerant gas with valve.Then, from the hyperbaric chamber side, by the discharge port of not drawing, process is formed at the discharge anechoic chamber 62 in the upper support portion material 54 again, and is discharged into the outside from refrigerant discharge tube 96.At this moment, refrigerant is compressed to suitable supercritical pressure.
The refrigerant gas that emits from refrigerant discharge tube flow into gas cooler 154, and after this sentences the heat release of air cooling mode, arrives aforementioned oil separator 170.At oil separator 170, refrigerant gas and separated the opening of oil.
Then, the oil of separating from refrigerant gas flow into oil circuit 175.After oil is set at capillary tube 176 decompression on the oil circuit 175, by second inner heat exchanger 162.Oil is just captured heat from the low voltage side refrigerant of first inner heat exchanger 160 herein and after being cooled, is returned in the compressor 10.
As mentioned above, because the oil of cooling gets back in the seal container 12 of compressor 10, so can be cooled off effectively by oil in the seal container 12.Therefore, the temperature that can suppress in the seal container 12 rises, and can promote the compression efficiency of the second rotation compression assembly 34.
In addition, the shortcomings such as pasta reduction of the accumulator in the seal container 12 also can be avoided.
On the other hand, the refrigerant gas that comes out from oil separator 170 passes through first inner heat exchanger 160.Refrigerant is seized heat in this place by low voltage side refrigerant, and is further cooled off.By passing the existence of an inner heat exchanger 160, heat is seized by low voltage side refrigerant, so can be lowered in the evaporating temperature of the refrigerant of vaporizer 157.Therefore, the cooling capacity of vaporizer just promotes.
Arrived the first expansion valve 156A of expansion mechanism 156 by the high pressure side refrigerant gas of first heat exchanger, 160 coolings.In addition, in the ingress of the first expansion valve 156A, refrigerant gas or gaseous state.As previously mentioned, the aperture of the first expansion valve 156A is adjusted to the suction side pressure (the middle pressure) that the pressure that makes refrigerant is higher than the second rotation compression assembly 34 of compressor 10.The pressure of pressing in the middle of herein, refrigerant just reduces pressure to and is higher than.Thus, a refrigerant part is liquefied, and becomes gas/liquid two-phase mixture, flow into gas-liquid separator 200 again.In this place, gas refrigerant and liquid refrigerant are separated.
Then, the liquid refrigerant in the gas-liquid separator 200 flow into injection loop 210.Liquid refrigerant is set at capillary tube 220 decompressions on the injection loop 210, and becomes the pressure of pressing a little more than the centre.Afterwards, through refrigerant ingress pipe 92, be injected into the suction side of the second rotation compression assembly 34 of compressor 10.Herein, the refrigerant evaporation utilizes and brings into play cooling action from absorbing heat on every side.Thus, comprising second compressor 10 that rotates compression assembly 34 itself just is cooled.
As above-mentioned, because refrigerant is depressurized at injection loop 210, be re-introduced into the suction side of the second rotation compression assembly 34 of compressor 10, and refrigerant is cooled the second rotation compression assembly 34 in this place's evaporation.Therefore, the second rotation compression assembly 34 can be cooled off effectively.By this kind mode, the compression efficiency of the second rotation compression assembly 34 can be raised.
On the other hand, the gas refrigerant that comes out from gas-liquid separator 200 arrives the second expansion valve 156B.The pressure of refrigerant by the second expansion valve 156B descends and carries out final liquefaction, and under the state of gas/liquid two-phase mixture inflow evaporator 157.In this place, refrigerant evaporation, utilization are absorbed heat from air and are brought into play cooling action.
As mentioned above, pressed refrigerant by intermediate cooling loop 150 in the middle of 32 compressions of the first rotation compression assembly, restrained the effect that temperature rises in the seal container 12 by making; Passed through second inner heat exchanger 162 by making from refrigerant gas by oil separator 170 isolated oil, suppress the effect that temperature rise in the seal container 12; More by coming divided gas flow refrigerant and liquid refrigerant with gas-liquid separator 200, after isolated liquid refrigerant is by capillary tube 220 decompressions, make it evaporation at the second rotation compression assembly 34 from heat absorption on every side, to cool off the effect of the second rotation compression assembly 34, the compression efficiency of the second rotation compression assembly 34 can be raised.In addition, utilize to make by the refrigerant of the second rotation compression assembly, 34 compressions by first inner heat exchanger 160, with the effect of the refrigerant evaporating temperature that reduces revaporizer 157, the refrigerant evaporating temperature of vaporizer 157 also be lowered by.
That is the evaporating temperature at the vaporizer 157 of this situation can for example reach the ultralow temperature scope below-50 ℃ at an easy rate.In addition, also can reduce the power consumption of compressor 10 simultaneously.
Afterwards, refrigerant flows out from vaporizer 157, by first inner heat exchanger 160. at this place, capture heat from aforementioned high pressure side refrigerant, and after being subjected to heat effect, arrive second inner heat exchanger 162. then, second inner heat exchanger 162 is captured heat from the oil that flows through oil circuit 175 again, more to be subjected to further heat effect.
Become low temperature in vaporizer 157 evaporations.The refrigerant that comes out from vaporizer 157 is not the perfect gas state, but is mixing liquid.By carrying out heat exchange by first inner heat exchanger 160 and high pressure side refrigerant, refrigerant is heated.Thus, refrigerant can almost completely become gas.Moreover by carrying out heat exchange by second inner heat exchanger 162 and oil, refrigerant can be heated, and has positively got temperature, and becomes gas fully.
Thus, the refrigerant that comes out from vaporizer 157 can positively be gasified.Particularly, even when under operating condition, producing residue refrigerant, utilize first inner heat exchanger 160 and second inner heat exchanger 162, heat low voltage side refrigerant with two stages, just can prevent positively that liquid refrigerant is inhaled into the liquid return phenomenon in the compressor 10 so can not need to be provided with absorption cell, and can avoid compressor 10 because the suffered damage of liquid compression.
Therefore, under discharge temperature that can not make compressor 10 or inside temperature rising, the degree of superheat can be guaranteed.Therefore, the reliability of moving the critical refrigerant circulation means can promote.
In addition, by the refrigerant of second inner heat exchanger, 162 heating, be inhaled into the first rotation compression assembly 32 of compressor 10 from refrigerant ingress pipe 94.This circulation operation repeatedly.
As mentioned above, possessing intermediate cooling loop 150, the refrigerant that the first rotation compression assembly 32 is given off is in gas cooler 154 heat releases; Oil separator 170 is separated oil from the refrigerant that is compressed by the second rotation compression assembly 34; Oil circuit 175 makes the oil decompression that is separated by oil separator 170 and gets back in the compressor; First inner heat exchanger 160, make that gas cooler 154 comes out from carrying out heat exchange between the refrigerant of the second rotation compression assembly 34 and the refrigerant that vaporizer 157 comes out; And second inner heat exchanger 162, carry out heat exchange between the refrigerant that comes from evaporator drier 157 that the oil that flows through oil circuit 175 and first inner heat exchanger 160 are come out.Expansion mechanism 156 as the throttling means is made of the first expansion valve 156A and the second expansion valve 156B that is arranged on the downstream side of the first expansion valve 156A.In addition, have more remarks entry loop 210, make the part refrigerant decompression of between the first expansion valve 156A and the second expansion valve 156B, flowing, in the suction side of the second rotation compression assembly 34 that is injected into compressor 10.Therefore, the refrigerant from the second rotation compression assembly 34 that the refrigerant that vaporizer comes out comes out at first inner heat exchanger 160 and gas cooler carries out heat exchange capturing heat, and carries out heat exchange to capture heat at second inner heat exchanger 162 and the oil that flows through oil circuit 175.Therefore, the degree of superheat of refrigerant can positively be guaranteed, to avoid the liquid compression in the compressor 10.
On the other hand, after the refrigerant from the second rotation compression assembly 34 that gas cooler is come out passes through oil separator 170, captured heat at first inner heat exchanger 160 by the refrigerant that vaporizer 157 comes out, the evaporating temperature of refrigerant is descended thus.Mode thus, the cooling capacity of the refrigerant gas of vaporizer 157 can promote.In addition, because possess intermediate cooling loop 150, so compressor 10 temperature inside can be lowered.
Compressor 10 temperature inside in addition, flow through the oil of oil circuit 175, after the refrigerant that comes from evaporator drier that second inner heat exchanger 162 is come out by first inner heat exchanger 160 is captured heat, return in the compressor 10, so can further be reduced.
Moreover, gas-liquid separation gas 200 being set between first and second expansion valve 156A, 156B, injection loop 210 will be reduced pressure by the liquid refrigerant that gas-liquid separator 200 separates, and is re-introduced into the suction side of the second rotation compression assembly 34 of compressor 10.Therefore, the refrigerant from injection loop 210 just evaporates and from heat absorption on every side, all can be cooled off effectively so comprise the compressor 10 of the second rotation compression assembly 34.Thus, the refrigerant evaporating temperature of the vaporizer 157 of refrigerant cycle can further reduce.
Mode from the above mentioned, it is possible making the refrigerant evaporating temperature reduction of the vaporizer 157 of refrigerant cycle, for example the evaporating temperature of vaporizer 157 can reach the ultralow temperature scope below-50 ℃ at an easy rate. and in addition, the power consumption of compressor 10 also can be lowered.
The 4th embodiment
Oil circuit 175A shown in Figure 5 is provided with capillary tube 176 too.But in this situation is through second inner heat exchanger 162, is connected to refrigerant ingress pipe 92, its be communicated to the second rotation compression assembly 34 casing top half 38 do not draw the suction path.Thus, can be fed to the second rotation compression assembly 34 by the oil of second inner heat exchanger, 162 coolings.
As above-mentioned, oil circuit 175A will be by oil separator 170 isolated oil with capillary tube 176 decompressions, after the refrigerant that comes from evaporator drier 157 that second inner heat exchanger, 162 places and first inner heat exchanger 160 come out carries out heat exchange, get back to the second rotation compression assembly of compressor 10 again from refrigerant ingress pipe 92.
Thus, the second rotation compression assembly 34 can be cooled off effectively, and the compression efficiency of the second rotation compression assembly 34 also can be raised.
In addition, because DFF Direct Fuel Feed is to the second rotation compression assembly 34, so can avoid the shortcoming of the low on fuel of the second rotation compression assembly 34.
Moreover, in the present embodiment,,, get back to the suction side of the second rotation compression assembly 34 again from refrigerant ingress pipe 92 to be arranged on the capillary tube decompression of injection loop 210 by 200 isolated liquid refrigerants of gas-liquid separator.But, also can not install gas-liquid separator 200.When this situation, the refrigerant that the first expansion valve 156A comes out is not (because there is gas-liquid separator, so the state of refrigerant is gas, liquid or its admixture), drop to suitable pressure (a little more than the pressure of centre pressure) with the capillary tube 220 that is arranged on injection loop 210, be inhaled into the suction side of the second rotation compression assembly 34 again from refrigerant ingress pipe 92.
Moreover the refrigerant that the first expansion valve 156A comes out is depressurized to suitable pressure (pressure of pressing a little more than the centre), and is gas at the refrigerant setting state of this situation, and capillary tube 220 is not need to be provided with.
In addition, in this embodiment, the oil separator 170 that separates means as oil is arranged on the refrigerant pipe arrangement between gas cooler 154 and first inner heat exchanger 160, still is not limited thereto framework.For example, also can be arranged on pipe arrangement between compressor 10 and the gas cooler 154.In addition, be arranged on oil circuit 175 and as the capillary tube 176 of decompression means, also can heat exchange pattern volume pay the refrigerant pipe arrangement that comes out in first inner heat exchanger 160, to constitute second inner heat exchanger 162.
Secondly, in an embodiment, refrigerant is to use carbon dioxide, but the present invention is not limited thereto.In the conversion critical refrigerant cycle, any spendable refrigerant, that is become the R23 (CHF that postcritical HFC is a refrigerant in the high pressure side 3) or nitrogen oxide (N 2O) etc. refrigerant all can be suitable for.In addition, be the R23 (CHF of refrigerant when using this HFC 3) or or nitrogen oxide (N 2During O) etc. refrigerant, the refrigerant evaporating temperature of vaporizer 157 can arrive the ultralow temperature below-80 ℃.
The 5th embodiment
Then, with reference to figure 6, describe another embodiment of conversion critical cooling circulation device of the present invention in detail.Fig. 6 illustrates the cryogen circuit figure of the conversion critical cooling circulation device of this situation.In addition, in Fig. 6, has identical or similar effect with Fig. 1 and Fig. 5 same-sign person.
The cryogen circuit of Fig. 5 and conversion critical cooling circulation device shown in Figure 6 different are in the high pressure side refrigerant by first inner heat exchanger 160 and arrive as the expansion valve 156. of throttling means then, the outlet of expansion valve 156 is connected to the inlet of vaporizer 157, the refrigerant pipe arrangement that vaporizer 157 comes out arrives second inner heat exchanger 162. then through first inner heat exchanger 160, the refrigerant pipe arrangement that second inner heat exchanger 162 comes out is connected to refrigerant ingress pipe 94.
High pressure side refrigerant gas by 160 coolings of first inner heat exchanger arrives expansion valve 156.In addition, in the ingress of expansion valve 156, refrigerant gas still is the state of gas.Refrigerant utilizes the pressure of expansion valve 156 to descend, and becomes gas/liquid two-phase mixture, and flow in the vaporizer 157 with this state.Refrigerant is in this place's evaporation and from the air heat absorption, with the performance cooling action.
At this moment, pressed refrigerant by intermediate cooling loop 150 in the middle of 32 compressions of first rotary compressor, suppressed the effect that temperature rises in the seal container 12 by making; Pass through second inner heat exchanger 162 by making from the isolated oil of refrigerant gas, suppress the effect that temperature rise in the seal container 12 with oil separator 170; The compression efficiency of the second rotation compression assembly 34 can promote.In addition, pass through first inner heat exchanger 160, be reduced in the effect of the refrigerant temperature of vaporizer 157, can reduce the evaporating temperature of the refrigerant of vaporizer 157 by making by the refrigerant gas of the second rotation compression assembly, 34 compressions.
That is the evaporating temperature of the vaporizer 157 under this situation can reach the low temperature range as-30 ℃ to-40 ℃ at an easy rate.In addition, also can reduce the consumes power of compressor 10 simultaneously.
Afterwards, refrigerant flows out from vaporizer 157, by first inner heat exchanger 160, and obtains heat at this from high pressure side refrigerant, and is subjected to heat effect, just arrives second inner heat exchanger 162 afterwards.Then,, return the lubricant oil on road 175, obtain heat, further to be subjected to heat effect from the oil of flowing through at second inner heat exchanger 162.
Become low temperature and be not to be entirely gaseous state in vaporizer 157 evaporation from the refrigerant that vaporizer comes out, but the state of mixing material.But, making it to carry out heat exchange by first inner heat exchanger 160 and high pressure side refrigerant, refrigerant is heated.Thus, refrigerant almost completely becomes gas.Moreover, make it pass through second inner heat exchanger 162, come to carry out heat exchange with oil, refrigerant is heated, and becomes gas fully positively to have got temperature.
Thus, the refrigerant that comes out from vaporizer 157 can positively be gasified.Particularly, even when under operating condition, producing residue refrigerant, utilize first inner heat exchanger 160 and second inner heat exchanger 162, heat low voltage side refrigerant with two stages, just can prevent positively that liquid refrigerant is inhaled into the liquid return phenomenon in the compressor 10 so can not need to be provided with absorption cell, and can avoid compressor 10 because the suffered damage of liquid return.
Therefore, under discharge temperature that can not make compressor 10 or inside temperature rising, the degree of superheat can be guaranteed.Therefore, the reliability of conversion critical cooling circulation device can promote.
In addition, by the refrigerant of second inner heat exchanger, 162 heating, be inhaled into the first rotation compression assembly 32 of compressor 10 from refrigerant ingress pipe 94.This circulation operation repeatedly.
As mentioned above, possessing intermediate cooling loop 150, the refrigerant that the first rotation compression assembly 32 is given off is in gas cooler 154 heat releases; First inner heat exchanger 160, make that gas cooler 154 comes out from carrying out heat exchange between the refrigerant of the second rotation compression assembly 34 and the refrigerant that vaporizer 157 comes out; Oil separator 170 is separated oil from the refrigerant that is compressed by the second rotation compression assembly 34; Oil circuit 175, the oil decompression with being separated makes it to return in the compressor 10; And second inner heat exchanger 162, make between oil that flows through oil circuit 175 and the refrigerant that comes from evaporator drier 157 that first inner heat exchanger 160 comes out and carry out heat exchange, the refrigerant that vaporizer 157 comes out can carry out heat exchange at the refrigerant from the second rotation compression assembly 34 that first inner heat exchanger 160 and gas cooler 154 come out capturing heat, and carries out heat exchange to capture heat at second inner heat exchanger 162 and the oil that flows through oil circuit 175.Therefore, the degree of superheat of refrigerant can positively be guaranteed, to avoid the liquid compression in the compressor 10.
On the other hand, after the refrigerant from the second rotation compression assembly 34 that gas cooler is come out passes through oil separator 170, captured heat at the first internal heat parallel operation 160 by the refrigerant that vaporizer 157 comes out, the evaporating temperature of refrigerant is descended thus. mode thus, the cooling capacity of the refrigerant gas of vaporizer 157 can promote. in addition, because possess intermediate cooling loop 150, so compressor 10 temperature inside can be lowered.
Compressor 10 temperature inside in addition, flow through the oil of oil circuit 175, after the refrigerant that comes from evaporator drier that second inner heat exchanger 162 is come out by first inner heat exchanger 160 is captured heat, return in the compressor 10, so can further be reduced.
Thus, the refrigerant evaporating temperature at the vaporizer of refrigerant cycle is reduced.For example, the evaporating temperature at vaporizer 157 places can arrive-30 ℃ to-40 ℃ low temperature range at an easy rate.In addition, the power consumption of compressor 10 also can reduce.
The 6th embodiment
Then, with reference to figure 7, describe another embodiment of conversion critical cooling circulation device of the present invention in detail.Fig. 7 illustrates the cryogen circuit figure of the conversion critical cooling circulation device of this situation.In addition, in Fig. 7, has identical or similar effect with Fig. 1 and Fig. 6 same-sign person.
Oil circuit 175A shown in Figure 7 is provided with capillary tube 176 too.But in this situation is through second inner heat exchanger 162, is connected to refrigerant ingress pipe 92, its be communicated to the second rotation compression assembly 34 casing top half 38 do not draw the suction path.Thus, can be fed to the second rotation compression assembly 34 by the oil of second inner heat exchanger, 162 coolings.
As above-mentioned, oil circuit 175A will be by oil separator 170 isolated oil with capillary tube 176 decompressions, after the refrigerant that comes from evaporator drier 157 that second inner heat exchanger, 162 places and first inner heat exchanger 160 come out carries out heat exchange, get back to the second rotation compression assembly of compressor 10 again from refrigerant ingress pipe 92.
Thus, the second rotation compression assembly 34 can be cooled off effectively, and the compression efficiency of the second rotation compression assembly 34 also can be raised.
In addition, because DFF Direct Fuel Feed is to the second rotation compression assembly 34, so can avoid the shortcoming of the low on fuel of the second rotation compression assembly 34.
In addition, in this embodiment, the oil separator 170 that separates means as oil still is not limited thereto framework for being arranged on the refrigerant pipe arrangement between the gas cooler 154 and first inner heat exchanger 160.For example, also can be arranged on pipe arrangement between compressor 10 and the gas cooler 154.In addition, be arranged on oil circuit 175 and as the capillary tube 176 of decompression means, also can heat exchange pattern volume pay the refrigerant pipe arrangement that comes out in first inner heat exchanger 160, to constitute second inner heat exchanger 162.
Secondly, in an embodiment, refrigerant is to use carbon dioxide, but the present invention is not limited thereto.Nitrogen oxide (N 2Any refrigerant that O) etc. can use in the conversion critical refrigerant cycle all can be suitable for.
The 7th embodiment
Then with reference to figure 8, above-mentioned compressor 10 constitutes the part of the cryogen circuit of hot-water supply device shown in Figure 8.That is the refrigerant discharge tube 96 of compressor 10 is connected to the inlet of gas cooler 154.Then, the pipe arrangement that comes out of gas cooler 154 arrives the expansion valve 156 as the throttling means.The outlet of expansion valve 156 is connected to the inlet of vaporizer 157, and the pipe arrangement that vaporizer 157 comes out is connected to refrigerant ingress pipe 94.
In addition, bypass circulation (the bypass loop) 180 that do not draw of Fig. 1 comes out from the difference midway of refrigerant ingress pipe 92.Bypass circulation 180 presses refrigerant gas with expansion valve 156 decompressions in the middle of seal container 12 not being discharged, and is supplied to the loop of vaporizer 157.Couple together with the refrigerant pipe arrangement between expansion valve 156 and the vaporizer 157.Then, being used for the solenoid valve 158 as control valve unit of this expansion circuit 180 of switch is arranged on the bypass circulation 180.
Then explanation possesses the action of the cryogen circuit device of above-mentioned formation. and in addition, before compressor 10 startings, solenoid valve 158 cuts out it with the control gear of not drawing.
Via terminal 20 and the distribution do not drawn, after stator coil 28 energisings of the electric assembly 14 of compressor 10, electric assembly 14 just starts and rotor 24 also rotates thereupon.Rotate by this, chimeric the last bottom roller 46,48 of the eccentric part up and down that is wholely set with running shaft 16 42,44 is eccentric rotation the in cylinder up and down just.
Thus, via the suction path 60 that is formed in refrigerant ingress pipe 94 and the lower support portion material 56, the suction port of never drawing is drawn into the low-pressure refrigerant gas of the low pressure chamber side of cylinder 40, can be by the action of roller 48 with valve, press in the middle of being compressed into, from the hyperbaric chamber side of following cylinder 40,, be discharged in the seal container 12 again from middle discharge tube 121 via the access of not drawing.Thus, pressure condition in the middle of seal container 12 just becomes.
Then, press refrigerant gas through refrigerant ingress pipe 92 in the middle of in the seal container 12, through the suction path do not drawn of stroke in upper support portion material 54, the suction port of never drawing is inhaled into the low voltage side of the casing top half 38 of the second rotation compression assembly 34 again.By the action of roller 46, carry out second section compression, to become the high pressure-temperature refrigerant gas with valve.Then, from the discharge port of hyperbaric chamber side,, be discharged into the outside from refrigerant discharge tube 96 via the discharge anechoic chamber 62 that is formed in the upper support portion material 54 by not drawing.
Refrigerant gas inflow gas cooler 154 from refrigerant discharge tube 96 is discharged after this place's heat release, arrives expansion valve 156.Refrigerant is depressurized at the expansion valve place, again in the inflow evaporator 157, and in this place from heat absorption on every side.Afterwards, be inhaled into the first rotation compression assembly 32 from refrigerant ingress pipe 94.Above-mentioned circulation is carried out repeatedly.
On the other hand, if long-time running, vaporizer 157 can frosting.In this situation, open solenoid valve 158 with the control gear of scheming not show, bypass circulation 180 is opened, to carry out the defrosting running of vaporizer 157.Thus, press in the middle of in the seal container 12 refrigerant gas to be back to the downstream side of expansion valve 156, flow directly into vaporizer 157 and be not depressurized.That is middle higher temperatures refrigerant of pressing can't be depressurized, but directly supplies vaporizer 157.Thus, vaporizer 157 just is heated and defrosts.
The high-pressure refrigerant of discharging from the second rotation compression assembly 34 does not reduce pressure and when supplying with evaporator defrost, because expansion valve 156 be a standard-sized sheet, and the suction pressure rising of the first rotation compression assembly 32.Thus, the head pressure of the first rotation compression assembly 32 (the middle pressure) uprises.This refrigerant is discharged by the second rotation compression assembly 34.But because expansion valve 156 standard-sized sheets, it is identical with the first rotation compression assembly 32 that the head pressure of the second rotation compression assembly 34 can become, so can generation pressure reverse phenomenon between the discharge side (high pressure) of the second rotation compression assembly 34 and suction side (low pressure).Yet, as mentioned above because from the first rotation compression assembly 32 discharge in the middle of press refrigerant to be removed from seal container 12, vaporizer 157 is defrosted, so the reverse phenomenon between the high pressure can prevent to defrost running time the and the middle pressure.
Pressure behavior when Fig. 9 illustrates compressor 10 starting of cryogen circuit device.As shown in Figure 9, when compressor 10 stopped, expansion valve 156 was a standard-sized sheet.Thus, before compressor 10 startings, the low pressure (suction side pressure of first rotary compressing device 32) in the cryogen circuit becomes by equalization (shown in the solid line) with high pressure (the discharge side pressure of the second rotation compression assembly 34).But middle press (dotted line) in the seal container 12 can't all be pressed at once, but as previously mentioned, can become than low voltage side, the high pressure in high pressure side.
According to the present invention, after compressor 10 starting, after after a while, with the control gear of not drawing solenoid valve 158 is opened, and made bypass circulation 180 open again.Thus, compressed and be discharged into seal container 12 interior a part of refrigerant gas to come out from refrigerant ingress pipe 92 by the first rotation compression assembly 32, by bypass circulation 180, inflow evaporator 157 again.
When by first rotation compression assembly 32 compression and be discharged into refrigerant gas in the seal container 12 not when bypass circulation 180 is run away to vaporizer 157, if make compressor 10 runnings at this state, back pressure can be added on the valve of the second rotation compression assembly 34, the discharge side pressure of the second rotation compression assembly 34 is identical with the suction side pressure meeting of the second rotation compression assembly 34, or the suction side pressure of the second rotation compression assembly 34 can be higher, so valve can pair roller 46 sides not produce elastic force, valve might fly up. therefore, the second rotation compression assembly 34 can can't compress. and compressor 10 becomes only remaining first compression assembly 32 in compression, and make compression efficiency worsen, (coefficient ofproduct COP) reduces also to cause the achievement coefficient of taking advantage of of compressor.
In addition, pressure difference in the middle of in the seal container 12 of the suction side pressure (low pressure) of the first rotation compression assembly 32 and the valve that is applied to the first rotation compression assembly 32 between the pressure can become greater than more than necessity, on the sliding parts of the front end of valve and roller 48 outer circumferential faces, the face pressure can apply up significantly, and valve and roller 48 become can wearing and tearing.The worst situation has the danger of damage.
Moreover, if pressing, the centres in the seal container 12 rise when most, because electric assembly 14 can get more high temperature, the suction of refrigerant gas, compress and each performance of a compressor such as discharging probably obstacle can take place.
But, as previously mentioned, utilize bypass circulation 180, when be discharged into by the first rotation compression assembly 32 seal container 12 in the middle of pressure refrigerant gas when running away to vaporizer 157, the middle pressure promptly reduced, and forces down than height and become, so can prevent to reverse phenomenon (with reference to figure 9).
By this, because can avoid the bumpy running behavior of aforementioned compressor 10, the performance of compressor 10 and durability can promote.Therefore, can keep the stable operational situation of cryogen circuit device, and then seek the lifting of the reliability of cryogen circuit device.
In addition, through after the scheduled time,, close solenoid valve 158 behind the solenoid valve 158 of open bypass circulation 180 with the control gear that does not illustrate.Just reply general normal operation afterwards.
As previously mentioned, utilize the bypass circulation 180 in aforementioned defrosting loop, the middle refrigerant gas of pressing in the seal container 12 can be run away to vaporizer 157 sides, so needn't revise pipe arrangement, also can avoid high pressure and middle pressure reverse phenomenon of pressing.Thus, cost of production can be lowered.
In addition, in the present embodiment, after compressor 10 startings,, open solenoid valve 158, to open bypass circulation 180 with the control gear that does not illustrate through preset time.But might not be confined to this framework.For example, as shown in figure 10,, open solenoid valve 158, after compressor 10 startings, close solenoid valve 158 again through a scheduled time with the control gear that does not illustrate from compressor 10 prestarts.Or, in compressor 10 startings, opens solenoid valve 158, and after a period of time warp, close solenoid valve.These a little situations all can avoid in the seal container 12 in the middle of press pressure reverse phenomenon between the high pressure with the discharge side of the second rotation compression assembly 34.
In addition, in the present embodiment, compressor uses bosom die mould multistage (two sections) compression type rotary compressor, but the present invention is not limited thereto framework.The multistage compression type compressor also can use.
The 8th embodiment
The intermediate cooling loop 150 that Fig. 1 does not draw be connected in parallel in refrigerant ingress pipe 92. intermediate cooling loops 150 be used for making by 32 compressions of first compression assembly and be discharged in the seal container 12 in the middle of press refrigerant gas in intermediate heat exchanger 151 heat releases, again refrigerant is drawn into afterwards in the second rotation compression assembly 34. in addition, aforementioned electric magnet valve 152 as control valve unit is arranged on the intermediate cooling loop 150, its be used for controlling the cryogen flow that given off by the first rotation compression assembly 32 to refrigerant ingress pipe 92 or flow into intermediate cooling loop 150. solenoid valves 152 according to effluent air temp sensor 190 detected second rotate the refrigerant temperature that compression assemblies 34 are discharged, when the discharge refrigerant temperature rises to a predetermined value (for example 100 ℃), just open solenoid valve 152, make refrigerant flow into intermediate cooling loop 150. when just closing solenoid valve 152 less than 100 ℃, make refrigerant flow into refrigerant ingress pipe 92. in addition, in an embodiment, as previously mentioned, come the switch of control electromagnetic valve 152 with same predetermined value, but the CLV ceiling limit value of opening solenoid valve 152 also can be different with the lower limit of closing solenoid valve. the aperture of solenoid valve 152 also can be done the adjustment in linearity or stage according to temperature variation.
Then explanation possesses the action of the cryogen circuit device of the present invention of above formation.In addition, before compressor 10 startings, utilize effluent air temp sensor 190 that solenoid valve 152 cuts out.
Via terminal 20 and the distribution do not drawn, after stator coil 28 energisings of the electric assembly 14 of compressor 10, electric assembly 14 just starts and rotor 24 also rotates thereupon.Rotate by this, chimeric the last bottom roller 46,48 of the eccentric part up and down that is wholely set with running shaft 16 42,44 is eccentric rotation the in cylinder up and down just.
Thus, via the suction path 60 that is formed in refrigerant ingress pipe 94 and the lower support portion material 56, the suction port of never drawing is inhaled into the low-pressure refrigerant of the low pressure chamber survey of cylinder 40, can be middle pressure condition and be by the action of roller 48 with valve.Hyperbaric chamber side from following cylinder 40 via the access of not drawing, is discharged in the seal container 12 from middle discharge tube 121.Thus, press in the middle of seal container 12 becomes.
As previously mentioned, because solenoid valve 152 is for cutting out, press refrigerant gas can all flow to refrigerant ingress pipe 92 in the middle of in the seal container 12.Then, through being formed at the suction path (not drawing) the upper support portion material 54, the suction port of never drawing is inhaled into the low pressure chamber side of the casing top half 38 of the second rotation compression assembly 34 from refrigerant ingress pipe 92.By the action of roller 46, carry out second section compression, and become the refrigerant gas of High Temperature High Pressure with valve.Afterwards, from the hyperbaric chamber side, by the discharge port of not drawing, the discharge anechoic chamber 62 via being formed in the upper support portion material 54 is discharged into the outside from refrigerant discharge tube.
This High Temperature High Pressure refrigerant gas is from gas cooler 154 heat releases, and the water in the hot water storage tank that heating is not drawn is to produce warm water.On the other hand, at gas cooler 154 places, itself is cooled refrigerant, is coming out from gas cooler 154.Then, after expansion valve 156 is depressurized, flow into vaporizer 157 evaporations (this moment is from heat absorption on every side), sucked back in the first rotation compression assembly 32 from refrigerant ingress pipe 94.Above-mentioned circulation is carried out repeatedly.
On the other hand, through behind the certain hour, utilize effluent air temp sensor 190, detect the refrigerant temperature of discharging from the second rotation compression assembly 34 when rising to 100 ℃, utilize effluent air temp sensor 190 that solenoid valve 152 is opened, open intermediate cooling loop 150.Thus, pressed refrigerant just to flow into intermediate cooling loop 150 in the middle of 32 compressions of the first rotation compression assembly, the discharge, and cooled off, be inhaled into the second rotation compression assembly 34 with the intermediate heat exchanger 151 that is arranged at this.
This state illustrates with the p-h line chart (Mo Liye line chart) of Figure 12.When the temperature of the refrigerant of discharging from the second rotation compression assembly 34 rises to 100 ℃, formed middle refrigerant (the state B of Figure 12) of pressing by 32 compressions of the first rotation compression assembly, by intermediate cooling loop 150, and the intermediate heat exchanger 151 that is set at this is captured (the state C of Figure 12) after the heat, is inhaled into the second rotation compression assembly 34.Then, by 34 compressions of the second rotation compression assembly, be discharged into compressor 10 outsides (the state E of Figure 12) again.In this situation, be TA2 shown in Figure 12 by second rotation compression assembly 34 compression and the refrigerant temperature that is discharged into compressor 10 outsides.
Even rise to 100 ℃ from second temperature of rotating the refrigerant of compression assembly 34 discharges, when refrigerant does not flow to intermediate cooling loop 150, the refrigerant (the state B of Figure 12) of being pressed in the middle of becoming by 32 compressions of the first rotation compression assembly can be directly by refrigerant ingress pipe 92, and be inhaled in the second rotation compression assembly 34 by 34 compressions of the second rotation compression assembly, be discharged into 10 ones on compressor (the state D of Figure 12) again. in this situation, the refrigerant temperature that is discharged into compressor 10 outsides by 34 compressions of the second rotation compression assembly then becomes TA1 shown in Figure 12, become the temperature height when flowing through intermediate cooling loop than refrigerant. therefore, temperature in the compressor 10 rises and makes compressor 10 overheated, so load increases. compressor 10 runnings become unstable, and because the hot environment in the seal container 12, make oily cracking, probably can have bad influence to the durability of compressor 10. still, as previously mentioned, by intermediate cooling loop 150, cool off by behind the refrigerant of the first rotation compression assembly, 32 compressions with intermediate heat exchanger 151, make refrigerant be inhaled into the second rotation compression assembly 34 again, just can suppress to be compressed by second rotary compressor, the temperature of the refrigerant that gives off rises.
Thus, risen by the temperature anomaly of second rotary compressor compression, the refrigerant that gives off and have harmful effect just can be avoided cooling circulation device.
Then, when being lower than 100 ℃, utilize gas temperature sensor 190, close solenoid valve 152, get back to the running that is just becoming as if the refrigerant temperature of being discharged that utilizes effluent air temp sensor 190 to detect by the second rotation compression assembly 34.
Thus, can't be inhaled into the second rotation compression assembly 34 by intermediate cooling loop 150 by the refrigerant of the first rotation compression assembly, 32 compressions, so in the process that 32 compressions of the first rotation compression assembly are sucked by the second rotation compression assembly 34 again, refrigerant temperature does not almost descend.Thus, refrigerant temperature is unlikely to descend a lot, just can avoid not making at gas cooler 154 places the shortcoming that high temperature warm water is brought.
As mentioned above, make the refrigerant ingress pipe 92 that is inhaled into the second rotation compression assembly 34 by the refrigerant of the first rotation compression assembly compression by possessing; The intermediate cooling loops 150 that connect side by side of refrigerant ingress pipe 92 therewith; And be used for controlling and make first cryogen flow that give off of rotation compression assembly 32 to refrigerant ingress pipe 92 or flow to the solenoid valve 152 of intermediate cooling loop 150, when the effluent air temp sensor 190 that is used for detecting the refrigerant temperature that emits from the second rotation compression assembly 34, the discharging refrigerant temperature that detects the second rotation compression assembly 34 is when rising to 100 ℃, solenoid valve 152 is just opened and is made cryogen flow arrive intermediate cooling loop 150, make compressor 10 overheated so can prevent the discharge refrigerant temperature abnormal ascending of the second rotation compression assembly 34, and then cause the running unsettled shortcoming, also can prevent the oily cracking that hot environment is caused in the seal container 12, and make the bad influence of the durability of compressor 10.
In addition, the discharging refrigerant temperature that effluent air temp sensor 190 detects the second rotation compression assembly 34 drops to when being lower than 100 ℃, because cutting out, solenoid valve 152 makes by the refrigerant of the first rotation compression assembly, 32 compressions directly by refrigerant ingress pipe 92, be inhaled into the second rotation compression assembly 34 again, so can be become high temperature by the temperature of the refrigerant gas of 34 compressions of the second rotation compression assembly and discharging.
Thus, during starting, the temperature of refrigerant can be easy to rise, and therefore the refrigerant that immerses compressor 10 also can promptly get back to normal state, and the startability of compressor can promote.
Thus, common about 100 ℃ hyperthermia induced cryogen passes back into gas cooler 154, so just can usually make the hot water of uniform temperature at gas cooler 154 places.Thus, the reliability of cooling circulation device can promote.
In addition, in the present embodiment, in the pipe arrangement between compressor 10 and gas cooler 154, detect the discharge refrigerant temperature of the second rotation compression assembly 34 of compressor 10 with effluent air temp sensor 190, with control electromagnetic valve 152, but be not limited thereto framework.For example, also can utilize time control electromagnetic valve 152.
In addition, in the present embodiment, compressor room's bosom type multistage (two sections) compression type rotary compressor, but the present invention is not limited thereto.For example, also can use the multistage compression type compressor.
The 9th embodiment
Extremely shown in Figure 15 as Figure 13, be communicated in the mode of utilizing pore processing in the seal container 12 with the through hole 131 of roller 46 inboards, making and bore a hole in the intermediate section dividing plate 36 of Fig. 1. Figure 13 is the planimetric map of intermediate section dividing plate 36, Figure 14 is the sectional arrangement drawing of intermediate section dividing plate 36, Figure 15 illustrates the expanded view of seal container 12 sides of through hole 131. that is, the gap is formed between intermediate section dividing plate 36 and the running shaft 16 slightly, the upside of this gap is communicated to roller 46 inboards (peripheral space of the eccentric part 42 of roller 46 inboards). moreover, the gap downside that intermediate section dividing plate 36 and running shaft are 16 is communicated to roller 48 inboards (peripheral space of the eccentric part 44 of roller 48 inboards). and through hole 131 is a path, make high pressure refrigerant gas from being formed at the upper support material 54 that is used for clogging the upside opening surface of side wheels 46 and cylinder 38 in the cylinder 38 and being used for clogging gap between the intermediate section dividing plate 36 of open lower side face, drain to roller 46 inboards (peripheral space of the eccentric part 42 of roller 46 inboards), flow into the gap and roller 48 inboards of 16 on intermediate section dividing plate 36 and running shaft again, run away to again in the seal container 12.
Drain to the high pressure refrigerant gas of roller 46 inboards, flow in the through hole 131 and flow out in the seal container 12 by being formed at gap between intermediate section dividing plate 36 and the running shaft 16.
Thus, the high pressure refrigerant gas that drains to roller 46 inboards can be run away in the seal container 12 from through hole 131, so can avoid high pressure refrigerant gas to be trapped in the gap between roller 46 inboards, intermediate section dividing plate 36 and the running shaft 16 and the shortcoming of roller 48 inboards.Thus, utilize pressure difference, just can oil be supplied to roller 46 inboards and roller 48 inboards from the oil supply hole 82,84 of aforesaid running shaft 16.
Particularly, only, the high pressure refrigerant gas that drains to roller 46 inboards can be run away in the seal container 12, so also can suppress the increase of processing cost to form the through hole 131 that connects intermediate section dividing plate 36 in the horizontal direction with doing one's utmost.
In addition, the intercommunicating pore (upright opening) 133 that extends at upside is arranged in the middle part of through hole 131.The intercommunicating pore 133 that is communicated with intermediate section dividing plate 36 is arranged in casing top half 38 with the injection that sucks port 161 (suction side of the second rotation compression assembly 34) with (injection) intercommunicating pore 134.The through hole 131 of intermediate section dividing plate 36 passes through aforesaid oil supply hole 82,84 in the opening of running shaft 16 sides, is communicated to the oilhole of not drawing.
In this situation, as described later, because press in the middle of becoming in the seal container 12, oil is difficult to be supplied in second section casing top half 38 that becomes high pressure.But, by intermediate section dividing plate 36 is made above-mentioned structure, oily accumulator from seal container 12 inner bottom parts is drunk up and is risen via the oilhole of not drawing, the oil that comes out from oil supply hole 82,84 can enter into the through hole 131 of intermediate section dividing plate 36, is supplied to the suction side (sucking port 161) of casing top half 38 again through intercommunicating pore 133,134.
L among Figure 16 is the pressure oscillation of the suction side in the expression casing top half 38.P1 represents the pressure of running shaft 16 sides of intermediate section dividing plate 36 among the figure.Shown in L1 among the figure, the pressure (suction pressure) of casing top half 38 suction sides utilizes to suck crushing in the process that sucks, and can be lower than the pressure of running shaft 16 sides of intermediate section dividing plate 36.During this period, oil passes through through hole 131, the intercommunicating pore 133 of intermediate section dividing plate 36 again, and is injected in the casing top half 38 from the intercommunicating pore 134 of cylinder 38 through the oilhole do not drawn in the running shaft 16 and from oil supply hole 82,84, and reaches the purpose of fuel feeding.
As above-mentioned, be used for making the high pressure refrigerant gas that drains to roller 46 inboards to run away to the intercommunicating pore (upright opening) 133 of the upside extension of the through hole 131 that forms in the seal container 12 by being formed at, and by the intercommunicating pore 133 of formation connection intermediate section dividing plate 36 and the injection intercommunicating pore 134 at the suction port 161 of casing top half 38, even being higher than, the pressure in the cylinder 38 of the second rotation compression assembly 34 becomes in the middle seal container 12 of pressing, utilize the suction crushing of the suction process of the second rotation compression assembly 34, the oil positively through hole from be formed at intermediate section dividing plate 36 131 is fed in the cylinder 38.
In addition, the through hole 131 that dual-purpose is used for making the high pressure of roller 46 inboards to escape, only by the intercommunicating pore 133 that extends from these through hole 131 upsides that in casing top half 38, forms and be used for being communicated with the suction port 161 of casing top half 38 and the intercommunicating pore 134 of intercommunicating pore 133, just can positively oil be supplied with the second rotation compression assembly 34.Therefore, can utilize simple structure and low cost to reach the lifting of compressor performance and the answer of reliability.
That is, can avoid the roller inboard 46 of the second rotation compression assembly 34 to become the shortcoming of high pressure, and can positively carry out the lubricated of second rotary compressor 34.So the performance of rotary compressor 10 can be guaranteed, and reliability can promote.
Moreover, as previously mentioned, because electric assembly 14 utilizes phase inverter to control rotating speed, can be started with low speed when making compressor start, so when rotary compressor 10 startings, even oil is inhaled into from the accumulator of through hole 131 by seal container 12 inner bottom parts, also can suppress the bad influence that causes because of liquid compression, also can avoid the problem that reliability reduces
Consideration is to influence, combustibility and the toxicity etc. of earth environment, and refrigerant uses the carbon dioxide (CO of nature refrigerant 2), enclose the oil product that seal container 12 interior oil as lubricant oil then for example use mineral oil, alkylbenzene oil (alkyl benzene), ester oil (ester oil), PAG oil (poly alkyl glycol, poly-alkyl glycol) etc. both to deposit.
At the suction path 58,60 of corresponding upper support portion material 54 and lower support portion material 56 and discharge on the position of anechoic chamber 62 and loam cake 66 upsides (positions of rough corresponding electric assembly 14 lower ends), bushing pipe 141,142,143 and 144 welds the side of the vessel 12A that is fixed in seal container 12 respectively.Bushing pipe 141,142 is an adjacency up and down, and bushing pipe 143 is positioned on the rough diagonal of bushing pipe 141.In addition, 144 of bushing pipes are on the position of departing from bushing pipe 141 about 90 degree.
An end that is used for importing the refrigerant conduit 92 of refrigerant gas in the casing top half 38 inserts and is connected in the bushing pipe 141, and an end of this refrigerant conduit 92 then is communicated in the suction path 58 of casing top half 38.Refrigerant conduit 92 arrives bushing pipe 144 through seal container 12 upsides, and the other end then inserts and is connected in the bushing pipe 144 and is communicated in the seal container 12.
In addition, be used for the end insertion of the refrigerant conduit 94 in the cylinder 40 under the refrigerant gas importing is connected in the bushing pipe 142, an end of this refrigerant conduit 94 then is communicated in down the suction path 60 of cylinder 40.In addition, refrigerant conduit 96 inserts and is connected in the bushing pipe 143, and an end of refrigerant conduit 96 is communicated to discharges anechoic chamber 62.
The action of above-mentioned formation then is described.In addition, rotary compressor 10 prestarts, the pasta in the seal container 12 generally is the opening upside of seal container 12 sides of the through hole 131 in being formed at intermediate section dividing plate 36.Therefore, the oil in the seal container 12 can flow in the through hole 131 from the opening of seal container 12 sides of through hole 131.
Via terminal 20 and the distribution do not drawn, utilize aforesaid phase inverter to make stator coil 28 energisings of electric assembly 14 after, electric assembly 14 just starts and rotor 24 also rotates thereupon.The starting of this moment is carried out as aforementioned low speed, gathers way afterwards again.Rotate by this, the last bottom roller 46,48 that the eccentric part up and down that is wholely set with running shaft 16 42,44 is chimeric, just off-centre is rotated in cylinder 38,40 up and down.
Thus, via the suction path 60 that is formed in refrigerant ingress pipe 94 and the lower support portion material 56, be drawn into the low-pressure refrigerant gas (4Mpa (MpaG)) of the low pressure chamber side of cylinder 40 from suction port 162, can be by the action of roller 48 with the valve of not drawing, press in the middle of being compressed into (8Mpa (MpaG)), again from the hyperbaric chamber side of following cylinder 40, discharge port 41, be formed on the discharge anechoic chamber 64 in the lower support portion material 56, be discharged in the seal container 12 from middle discharge tube 121 through access 63.
Then, press refrigerant gas to come out in the middle of in the seal container 12, via refrigerant ingress pipe 92 and be formed at suction path 58 in the upper support portion material 54, be inhaled into the low pressure chamber side of casing top half 38 from sucking port 161 from bushing pipe 144.
On the other hand, after rotary compressor 10 starting, the oil of invading from the opening of seal container 12 sides of aforementioned through hole 131 can be inhaled into the low pressure chamber side of the cylinder 38 of the second rotation compression assembly 34 via intercommunicating pore 133,134.Then, be inhaled into the middle refrigerant gas and the oil of pressing of cylinder 38 low pressure chamber sides, can carry out second section compression by the action of roller 46 with the valve of not drawing.At this, refrigerant gas becomes High Temperature High Pressure (12Mpa (MpaG)).
In this situation, the oil of pressing refrigerant gas to invade from the opening of seal container 12 sides of aforementioned through hole 131 with the centre also can be compressed, but since the revolution of rotary compressor 10 when being controlled in starting with low-speed running, so moment is less.Therefore, even oil is compressed, rotary compressor 10 almost is not affected yet, so can normally turn round.
Then, with the expectant control pattern, revolution is risen, last electric assembly 14 turns round with the revolution of expection. and the pasta in the running is at the downside of through hole 131. still, from aforementioned through hole 131, through intercommunicating pore 133 and intercommunicating pore 134, oil is supplied to the suction side of the second rotation compression assembly 34, so can avoid the oily insufficient shortcoming of the slide part of the second rotation compression assembly 34.
As mentioned above, be arranged in the intermediate section dividing plate 36 being communicated with seal container 12 interior through holes 131 with roller 46 inboards, and in the cylinder 38 that constitutes the second rotation compression assembly 34, perforation forms the through hole 131 that is used for being communicated with intermediate section dividing plate 36 and rotates the intercommunicating pore 133,134 of the suction side of compression assembly 34 with second.Therefore, the high pressure refrigerant gas that drains to roller 46 inboards from then on through hole 131 run away in the seal container 12.
Thus, utilize the pressure difference of roller 46 inboards and roller 48 inboards, supply with oil smooth-goingly from the oil supply hole 82,84 of running shaft 16.Therefore, the low on fuel of eccentric part 44 peripheries of eccentric part 42 peripheries of roller 46 inboards and roller 48 inboards just can be avoided.
In addition, even becoming, the pressure in the cylinder 38 of the second rotation compression assembly 34 is higher than the pressure status that becomes in the middle seal container of pressing 12, in the suction process of the second rotation compression assembly 34, utilize and suck crushing, can be positively with oil from be communicated with the intercommunicating pore 133,134 that forms with the through hole 131 of intermediate section dividing plate 36, supply in the cylinder 38.
Must, utilize better simply structure, avoid roller 46 inboards to become the shortcoming of high pressure, positively to carry out the lubricated of second rotary compressor 34.Therefore, the performance of rotary compressor 10 can guarantee that reliability also can promote.
Moreover, because electric assembly 14 is the revolution control type motor that starts with low speed when starting, so, when rotary compressor 10 startings, even oil is just drunk up from through hole 131 and from the accumulator of seal container 12 inner bottom parts, also can suppress the bad influence of liquid compression, and also can avoid the reduction of reliability.
In addition, in the present embodiment, the upside that is formed at the gap of 16 on intermediate section dividing plate 36 and running shaft is communicated to roller 46 inboards, and downside then is communicated to the inboard of roller 48, but not limited thereto kenel.For example, the upside that also can only be formed at the gap of 16 on intermediate section dividing plate 36 and running shaft is communicated to the situation (downside is not linked roller 48 inboards) of roller 46 inboards.In addition, the roller 46 inboard situations of cutting apart with intermediate section dividing plate 36 with roller 48 inboards also have no relations.In this situation, utilize middle part at the through hole 131 of intermediate section dividing plate 36, form and the roller 46 inboard axis direction holes that are communicated with, the high pressure of roller 46 inboards also can be run away in the seal container 12.Moreover oil also can supply to the suction side of second compression assembly 34 from oil supply hole 82.
In addition, in the present embodiment, the volume of the first rotation compression assembly is that the volume of the 2.89cc and the second rotation compression assembly is that the rotary compressor 10 of 1.88cc is used for explanation, but is not limited to above-mentioned volume size, and the rotary compressor of other volume also can use.
In addition, in the present embodiment, rotary compressor is done explanation with two sections compression type rotary compressors that possess the first rotation compression assembly and the second rotation compression assembly.But the present invention is not limited to this framework.The rotation compression assembly also can be to possess three sections, four sections or above rotation compression assembly.
The tenth embodiment
Then according to graphic the tenth embodiment that stupid invention is described.Figure 17 is as the rotary compressor of present embodiment, and the bosom that possesses first and second rotation compression assembly 32,34 is pressed the sectional arrangement drawing of multi-section type (two sections) compression type rotary compressor 10.In 17 figure, possess identical or similar effect with the member of Fig. 1 same-sign, its explanation is omitted and is not illustrated.
As shown in figure 17, the suction port of not drawing respectively with cylinder 38,40 about 38, the 40 inboard suction paths 58,60 that are communicated with of cylinder up and down are arranged in.The discharge port of never drawing utilizes the depressed part of upper support portion material 54 to clog the discharge anechoic chamber 62 that forms at the refrigerant that is compressed by casing top half 38 as the lid of keeping away face and is arranged in the upper support portion material 54.That is, discharge anechoic chamber 62 and seal as the loam cake 65 of the wall that is separated out this discharge anechoic chamber 62.
On the other hand, the discharge port that the refrigerant of cylinder 40 compressions is never drawn under the quilt, be discharged into tossing about in the discharge anechoic chamber 64 of position of being formed at lower support portion material 56 with electric assembly 14. discharge anechoic chamber 64 by being constituted of being used for covering lower support portion material 56 with the toss about lid 65 of position of electric assembly 14. the center of lid 65 has hole, is used for connecting running shaft 16 and is used for the double bearing 56A. that does the lower support portion material 56 of running shaft 16 bearings
In this situation, the upright central authorities that are located at upper support portion material 54 of bearing 56A.In addition, aforesaid bearing 56A breakthrough form is formed in the central authorities of lower support portion material 56.Running shaft 16 is kept by the bearing 56A of the bearing 54A of upper support portion material 54 and lower support portion material 56.
Then, discharge anechoic chamber 64 and the seal container 12 of the first rotation compression assembly 32 are interior is communicated with access.This access is a hole of not drawing, and it connects lower support portion material 56, upper support portion material 54, loam cake 66, cylinder 38,40 and intermediate section dividing plate 36 up and down.In this situation, the middle discharge tube 121 upright upper ends of being located at access, and the middle refrigerant of pressing just is discharged in the seal container 12 from this centre discharge tube 121.
In addition, loam cake 66 is distinguished to draw and is discharged the discharge anechoic chamber 62 that port and second rotates casing top half 38 internal communication of compression assembly 34.Electric assembly 14 and loam cake 66 are arranged on the upside of loam cake 66 at a distance of predetermined interval.Loam cake 66 is made of the circular steel plate that slightly becomes round (doughnut), and formation one hole it on is used for being communicated with the bearing 54A of above-mentioned upper support portion material 54.
In addition, enclose the oil product that seal container 12 interior oil as lubricant oil then for example use mineral oil, alkylbenzene oil (alkyl benzene), ester oil (ester oil), PAG oil (poly alkyl glycol, poly-alkyl glycol) etc. both to deposit.
At the suction path 58,60 of corresponding upper support portion material 54 and lower support portion material 56 and discharge on the position of anechoic chamber 62 and loam cake 66 upsides (positions of rough corresponding electric assembly 14 lower ends), bushing pipe 141,142,143 and 144 welds the side of the vessel 12A that is fixed in seal container 12 respectively.Bushing pipe 141,142 is an adjacency up and down, and 143 of bushing pipes are on the rough diagonal of bushing pipe 141.In addition, 144 of bushing pipes are on the position of departing from bushing pipe 141 about 90 degree.
An end that is used for importing the refrigerant conduit 92 of refrigerant gas in the casing top half 38 inserts and is connected in the bushing pipe 141, and an end of this refrigerant conduit then is communicated in the suction path 58 of casing top half 38.Refrigerant conduit 92 arrives bushing pipe 144 through seal containers 12 upsides, and the other end then inserts and is connected in the bushing pipe 144 and is communicated in the seal container 12.
In addition, be used for the end insertion of the refrigerant conduit 94 in the cylinder 40 under the refrigerant gas importing is connected in the bushing pipe 142, an end of this refrigerant conduit then is communicated in down the suction path 60 of cylinder 40.In addition, refrigerant conduit 96 inserts and is connected in the bushing pipe 143, and an end of refrigerant conduit is communicated to drain passageway 80 described later.
Aforementioned drain passageway 80 is communicated with the path of discharging anechoic chamber 62 and refrigerant discharge tube 96.This drain passageway 80 difference from the way of reservoir 100 is come out, and extends and form toward substantially horizontal in casing top half 38.One end of refrigerant discharge tube 96 inserts and is connected to this drain passageway 80.
Then, just by this drain passageway 80, be discharged into the outside of rotary compressor 10 by second refrigerant that rotates compression assembly 34 compressions and be discharged into discharge anechoic chamber 62 from refrigerant discharge tube 96.
In addition, aforementioned reservoir 100 is formed at down positions (sucking path 60 part in addition) in the cylinder 40 and suction path 60 opposition sides second compression assembly 34.This reservoir 100 is configured to up/down perforation casing top half 38, intermediate section dividing plate 36 and following cylinder 40.The upper end of this reservoir 100 is communicated to discharges anechoic chamber 62, and then following supporting portion, lower end material 56 is sealed.Then, aforesaid drain passageway 80 is communicated to a shade below the position of reservoir 100 upper ends.
In addition, return path 110 is from coming the difference setting a little more than the position of these reservoir 100 lower ends. and return path 110 is from reservoir 100 (seal container 12 sides) laterally, toward the hole that substantially horizontal is extended. restriction material 103 is a pore, and be formed in the return path 110, to reach throttling function. thus, return path 110 is by restriction material 103, be communicated with reservoir 100 inner and seal container 12 inside. then, the oil that is accumulated in reservoir 100 bottoms just passes through the pore of the restriction material 103 in the return path 110. and in this process, oil is depressurized and flows out in the seal container 12. and the oil of outflow just turns back to the accumulator 12C. of seal container 12 inner bottom parts
Utilization is formed at above-mentioned reservoir 100 in the rotary compressor structure 18, and the refrigerant gas of being discharged by second rotation compression assembly 34 compression and oil just flow in the reservoir 100 after discharge anechoic chamber 62 and be discharged.At this moment, refrigerant gas is towards drain passageway 80, and oil just flows directly to the below of reservoir 100.By the way, just separated from second oil that is discharged from of rotation compression assembly 34 smooth-goingly, and be accumulated to the below of reservoir 100 with refrigerant gas.Therefore, the oil mass that is discharged into rotary compressor 10 outsides just is minimized, and can prevent because big gauging flows out to the shortcoming of the freeze cycle decreased performance that is caused in the cryogen circuit of freeze cycle.
In addition, the oil that is accumulated in the reservoir 100 more sees through the return path 110 with restriction material 103, oil is turned back to be formed at the accumulator 12C of the bottom in the seal container 12, so can avoid the shortcoming of the low on fuel in the seal container 12C.
Generally speaking, can reduce the oily amount that is discharged in the refrigerant circulation circuit with doing one's utmost, and oil can be fed in the seal container 12 smooth-goingly.Therefore, the performance of rotary compressor 10 and reliability just can promote.
Moreover reservoir 100 forms with the through hole of cylinder 38,40 up and down to connect intermediate section dividing plate 36 up and down, so can simply construct, reduction oil is discharged into rotary compressor 10 outsides with doing one's utmost.
In addition, reservoir 100 is formed on down in the cylinder 40, and the position with following cylinder 40 in the position of suction path 60 opposition sides on.Therefore, the space utilization efficiency can promote.
Follow the action that above-mentioned formation is described.Via terminal 20 and the distribution do not drawn, after stator coil 28 energisings of the electric assembly 14 of compressor 10, electric assembly 14 just starts and rotor 24 also rotates thereupon.Rotate by this, chimeric the last bottom roller 46,48 of the eccentric part up and down that is wholely set with running shaft 16 42,44 is eccentric rotation the in cylinder up and down just.
Thus, via the suction path 60 that is formed in refrigerant ingress pipe 94 and the following cylinder 40, be drawn into down the low-pressure refrigerant gas of the low pressure chamber side of cylinder 40 from the suction port, can be by the action of roller 48 with valve, press in the middle of being compressed into, again from the hyperbaric chamber side of cylinder 40 down, through discharging the port, discharging anechoic chamber 64, through access, be discharged in the seal container 12 from middle discharge tube 121.Thus, become middle the pressure in the seal container 12.
Then, the middle refrigerant of pressing in the seal container 12 comes out from bushing pipe 144, and via the suction path 58 that is formed in refrigerant ingress pipe 92 and the casing top half 38, the suction port of never drawing is inhaled into the low pressure chamber side of casing top half 38.Press refrigerant to utilize the action of roller 46 and valve in the middle of being inhaled into, carry out second section compression, to become the refrigerant gas of High Temperature High Pressure.Then, from the discharge port of hyperbaric chamber side, be discharged into the discharge anechoic chamber 62 that is formed in the upper support portion material 54 by not drawing.
At this moment, the oil that supplies to the second rotation compression assembly 34 can be mixed in by in the refrigerant gas of the second rotation compression assembly, 34 compressions, makes oil also be discharged into and discharges anechoic chamber 62.Then, be discharged into refrigerant gas of discharging anechoic chamber 62 and the oil of sneaking in this refrigerant gas and can arrive reservoir 100.After entering into reservoir 100, refrigerant gas is towards drain passageway 80, the oily then separated as previously mentioned below of opening and accumulate on reservoir 100.The oil that is accumulated in reservoir 100 then just passes through aforesaid return path 110, flow into restriction material 103.The oil that flow into restriction material 103 is depressurized herein, flows out in the seal container 12 again.The oil that flows out is just got back to the vessel 12A wall of seal container 12, the accumulator 12C of seal container 12 bottom surfaces that surrounded such as cylinder 40 and lower support portion material 56 down.On the other hand, refrigerant gas through refrigerant discharge tube, is discharged into the outside of rotary compressor 10 from drain passageway 80.
As previously mentioned, be used for together being separated with the reservoir of accumulating 100 and be formed on the rotary compressor structure 18 from second oil that emits of rotation compression assembly 34 with refrigerant gas, and this reservoir 100 is communicated in the seal container 12 via the return path 110 that possesses restriction material 103. therefore, can reduce oil with the oil mass that is discharged into rotary compressor 10 outsides by the refrigerant gas of the second rotation compression assembly, 34 compressions.
Thus, because of big gauging flows out in the cryogen circuit of freeze cycle the shortcoming of freeze cycle mis-behave can be prevented with doing one's utmost.
In addition because reservoir 100 be formed on down in the cylinder 40 with the positions that suck path 60 opposition sides on, so space efficiency can promote.
Moreover, because reservoir 100 is as up/down perforation intermediate section dividing plate 36, the through hole of cylinder 38,40 up and down, reduces oil with doing one's utmost and flow to the compressor outside so can simply construct.
In addition, in the present embodiment, the drain passageway 80 of the second rotation compression assembly 34 is formed in the casing top half 38, and this drain passageway 80 is discharged into outside structure through refrigerant discharge tube 96.But, the present invention is not limited thereto framework.For example, the drain passageway 80 of the second rotation compression assembly 34 is formed at framework in the upper support portion material 54, is applicable to the present invention too.
In this situation, also can make the upper end of reservoir 100 connect channel and discharge in the anechoic chamber 62, or be communicated to out behind the discharge anechoic chamber 62 vent pathway 80 midway.
In addition, in the present embodiment, return path 110 is made the structure that is arranged on down in the cylinder 40, but is not limited thereto.For example also can be formed in the lower support portion material 56.
In addition, in the present embodiment, rotary compressor is done explanation with two sections compression type rotary compressors that possess the first rotation compression assembly and the second rotation compression assembly.But the present invention is not limited to this framework.The rotation compression assembly also can be to possess three sections, four sections or above rotation compression assembly.
As mentioned above, according to one embodiment of the invention, the compressor in the cooling circulation device, gas cooler, throttling means are connected in regular turn with vaporizer, and become supercritical pressure in the high pressure side.Cooling circulation device comprises with lower member.Aforementioned compressor is in seal container, have more the moving assembly of power backup and by first and second rotation compression assembly that electric assembly drove, be compressed sucking in the second rotation compression assembly by the first rotation compression assembly compression and the refrigerant of discharging, and be discharged in the gas cooler.Intermediate cooling loop makes the refrigerant of discharging from the first rotation compression assembly, in the gas cooler heat release.First inner heat exchanger makes from gas cooler to come out and carry out heat exchange from the second rotation refrigerant of compression assembly and the refrigerant that vaporizer comes out.Second inner heat exchanger gas cooler is come out and the intermediate cooling loop flowing refrigerant with come out and come the refrigerant of from evaporator drier to carry out heat exchange from first inner heat exchanger.Therefore, the refrigerant that comes out from vaporizer carries out heat exchange at the refrigerant that flows through intermediate cooling loop that first inner heat exchanger and gas cooler come out, to capture heat.Therefore, the degree of superheat of refrigerant can be positively kept, and liquid compression can be avoided at compressor.
On the other hand, gas cooler come out from the refrigerant of the second rotation compression assembly at first inner heat exchanger, capture heat from the refrigerant that vaporizer comes out, with this refrigerant temperature is descended.Thus, the cooling capacity of the refrigerant gas of vaporizer can promote.That is, do not increasing under the refrigerant circulation quantity, can reach desired evaporating temperature easily, also can reach the purpose that reduces compressor power consumption.
In addition, because possess intermediate cooling loop, so the compressor temperature inside can descend.Particularly in this situation, the refrigerant that flows through intermediate cooling loop gives the refrigerant of from evaporator drier with heat, in being inhaled into the second rotation compression assembly after the gas cooler heat release.Therefore, can not produce because of the compressor inside temperature rising that second inner heat exchanger produces is set.
In above-mentioned cooling circulation device, because refrigerant uses carbon dioxide, so environmental problem is contributed to some extent.
In above-mentioned cooling circulation device, the evaporating temperature of the refrigerant of vaporizer is very effective at+12 ℃ to-10 ℃.
According to another embodiment of the present invention, the compressor in the cooling circulation device, gas cooler, throttling means are connected in regular turn with vaporizer, and become supercritical pressure in the high pressure side.Cooling circulation device comprises with lower member.Aforementioned compressor is in seal container, have more the moving assembly of power backup and by first and second rotation compression assembly that electric assembly drove, be compressed sucking in the second rotation compression assembly by the first rotation compression assembly compression and the refrigerant of discharging, and be discharged in the gas cooler.Intermediate cooling loop makes the refrigerant of discharging from the first rotation compression assembly, in the gas cooler heat release.Oil separation means, in order to oil from being separated the refrigerant of the second rotation compression assembly.Oil circuit will be separated the oil decompression that means are separated by oil, and oil is got back in the compressor.First inner heat exchanger makes from gas cooler to come out and carry out heat exchange from the second rotation refrigerant of compression assembly and the refrigerant that vaporizer comes out.Second inner heat exchanger makes the oil that flows at oil circuit and comes out from first inner heat exchanger and come the refrigerant of from evaporator drier to carry out heat exchange.The second throttling means in first throttle means downstream side are constituted the throttling means by first throttle means and position.The part refrigerant of injection loop in order to will between first and second throttling means, flowing, be injected into compressor second the rotation compression assembly the suction side.Therefore, the refrigerant that comes out from vaporizer carries out heat exchange to capture heat at the refrigerant that flows through intermediate cooling loop that first inner heat exchanger and gas cooler come out, and carry out heat exchange at second inner heat exchanger and the oil that flows through oil circuit, to capture heat.Therefore, the degree of superheat of refrigerant can be positively kept, and liquid compression can be avoided at compressor.
On the other hand, gas cooler come out from the refrigerant of the second rotation compression assembly at first inner heat exchanger, capture heat from the refrigerant that vaporizer comes out, with this refrigerant temperature is descended.In addition, because possess intermediate cooling loop, so the compressor temperature inside can descend.
In addition, the oil that flows through oil circuit returns in the compressor after the refrigerant that comes from evaporator drier that second inner heat exchanger is come out by first inner heat exchanger is captured heat, so the compressor temperature inside can further reduce.
Moreover because flow through part refrigerant between first and second throttling means, the suction side of the second rotation compression assembly by being injected into compressor behind the injection loop again is so utilize the refrigerant of this injection can cool off the second rotation compression assembly.Thus, the compression efficiency of the second rotation compression assembly can be improved, and the temperature of compressor itself also can further descend.Therefore, in the refrigerant cycle, the refrigerant evaporating temperature at vaporizer is descended.
That is, by making the middle refrigerant of pressing that is compressed by first rotary compressor, to restrain the effect of the temperature rising in the seal container by intermediate cooling loop; Pass through second inner heat exchanger by making from the isolated oil of refrigerant, to restrain the effect of the temperature rising in the seal container with oil separator; And more by making the part refrigerant that flows through pipe arrangement between first and second throttling means be injected into the suction side of the second rotation compression assembly of compressor, to evaporate from heat absorption on every side, make the effect of second rotary compressor cooling etc., the compression efficiency of the second rotation compression assembly can promote.In addition, by making by the second rotation refrigerant gas that compression assembly compressed by first inner heat exchanger, with the effect of the refrigerant evaporating temperature that is reduced in vaporizer, the cooling capacity of vaporizer can promote significantly, and the power consumption of compressor also can reduce.
In aforesaid cooling circulation device, more comprise the gas-liquid separation means being set between first and second throttling means.Injection loop will be reduced pressure by the liquid refrigerant that the gas-liquid separation means are separated, and is re-introduced into the suction side of the second rotation compression assembly of compressor.Therefore, with from heat absorption on every side, the compressor itself that comprises the second rotation compression assembly can further and effectively be cooled off from the evaporation of the refrigerant of infusion circuit.Thus, the refrigerant evaporating temperature of the vaporizer in the refrigerant cycle can further reduce.
In aforesaid cooling circulation device, oil circuit makes to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place and carries out heat exchange, returns in the seal container of compressor.Therefore, utilize this oil can reduce the interior temperature of seal container of compressor effectively.
In aforesaid cooling circulation device, oil circuit makes to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place and carries out heat exchange, returns second this suction side that rotates compression assembly of compressor.Therefore, can lubricate the second rotation compression assembly on one side improving compression efficiency, and can reduce the temperature of compressor itself effectively.
It is the R23 of refrigerant, any refrigerant in the nitrogen oxide that refrigerant in the aforementioned cooling circulation device can use carbon dioxide, HCF, so environmental problem is contributed to some extent.
In addition, in above-mentioned cooling circulation device, the evaporating temperature of the refrigerant of vaporizer is very effective below-50 ℃.
According to another embodiment of the present invention, the compressor in the cooling circulation device, gas cooler, throttling means are connected in regular turn with vaporizer, and become supercritical pressure in the high pressure side.Cooling circulation device comprises with lower member.Aforementioned compressor is in seal container, have more the moving assembly of power backup and by first and second rotation compression assembly that electric assembly drove, be compressed sucking in the second rotation compression assembly by the first rotation compression assembly compression and the refrigerant of discharging, and be discharged in the gas cooler.Intermediate cooling loop makes the refrigerant of discharging from the first rotation compression assembly, in the gas cooler heat release.First inner heat exchanger makes from gas cooler to come out and carry out heat exchange from the second rotation refrigerant of compression assembly and the refrigerant that vaporizer comes out.Oil separation means in order to oil from being separated the refrigerant of the second rotation compression assembly.Oil circuit will be separated the oil decompression that means are separated by oil, and oil is got back in the compressor.Second inner heat exchanger makes the oil that flows at oil circuit and comes out from first inner heat exchanger and come the refrigerant of from evaporator drier to carry out heat exchange.Therefore, the refrigerant that comes out from vaporizer carries out heat exchange to capture heat at the refrigerant that flows through intermediate cooling loop that first inner heat exchanger and gas cooler come out, and carry out heat exchange at second inner heat exchanger and the oil that flows through oil circuit, to capture heat.Therefore, the degree of superheat of refrigerant can be positively kept, and liquid compression can be avoided at compressor.
On the other hand, gas cooler come out from the refrigerant of the second rotation compression assembly at first inner heat exchanger, capture heat from the refrigerant that vaporizer comes out, with this refrigerant temperature is descended.In addition, because possess intermediate cooling loop, so the compressor temperature inside can descend.
In addition, the oil that flows through oil circuit returns in the compressor after the refrigerant that comes from evaporator drier that second inner heat exchanger is come out by first inner heat exchanger is captured heat, so the compressor temperature inside can further reduce.Thus, the refrigerant temperature of the vaporizer in the refrigerant cycle can be lowered.
That is, by making the middle refrigerant of pressing that is compressed by first rotary compressor, to restrain the effect of the temperature rising in the seal container by intermediate cooling loop; And by making with oil separator from the isolated oil of refrigerant by second inner heat exchanger, the effect that rises with the temperature of restraining in the seal container etc., the compression efficiency of the second rotation compression assembly can promote.In addition, by making by the second rotation refrigerant gas that compression assembly compressed by first inner heat exchanger, with the effect of the refrigerant evaporating temperature that is reduced in vaporizer, the cooling capacity of vaporizer can promote significantly, and the power consumption of compressor also can reduce.
In aforesaid cooling circulation device, oil circuit makes to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place and carries out heat exchange, returns in the seal container of compressor.Therefore, utilize this oil can reduce the interior temperature of seal container of compressor effectively, the temperature that also can suppress in the seal container rises.
In aforesaid cooling circulation device, oil circuit makes to be separated by oil between the refrigerant that comes from evaporator drier that oil that means separate and first inner heat exchanger come out at the second inner heat exchanger place and carries out heat exchange, return this suction side of the second rotation compression assembly of compressor. therefore, the second rotation compression assembly can be lubricated on one side improving compression efficiency, and the temperature of compressor itself can be reduced effectively.
In above-mentioned cooling circulation device, because refrigerant uses carbon dioxide, so environmental problem is contributed to some extent.
In above-mentioned cooling circulation device, the evaporating temperature of the refrigerant of vaporizer is very effective at-30 ℃ to-40 ℃.
According to another embodiment of the present invention, the compressor in the cooling circulation device possesses and is driven first and second rotation compression assembly that assembly drives.Be compressed sucking in this second rotation compression assembly by the first rotation compression assembly compression and the refrigerant of discharging, and be discharged in this gas cooler.Bypass circulation under the refrigerant decompression that will not discharge from the first rotation compression assembly of compressor, supplies to vaporizer to refrigerant; And control valve unit, in order to when the evaporator defrost, open this bypass circulation.Control valve unit is also opened the stream of this bypass circulation when this compressor start.Therefore, when vaporizer defrosts, open control valve unit, the refrigerant of discharging from first compression assembly flows through bypass circulation, under not reducing pressure, supplies with and heats to vaporizer.
Thus, when the supply vaporizer defrosts when the high-pressure refrigerant of discharging from the second rotation compression assembly not being reduced pressure, the suction side of the second rotation compression assembly when turning round of can avoiding defrosting and the pressure reverse phenomenon of discharge side.
In addition, when compressor start, control valve unit is also open, and through bypass circulation, the discharge side of first compression assembly, that is the pressure of second compression assembly suction side can be run away to vaporizer.The phenomenon that the pressure of the discharge side (high pressure) of the suction side of the second rotation compression assembly in the time of therefore, can avoiding compressor start (the middle pressure) and second compression assembly reverses.
Thus, because can avoid the unsettled running behavior of compressor, can promote the performance and the durability of compressor.Therefore, can keep the steady running of cryogen circuit device, also can promote the reliability of cryogen circuit device.
Particularly, utilization is employed bypass circulation when defrosting, can make the refrigerant of discharging be discharged into the compressor outside from the first rotation compression assembly, so needn't change the establishing pipe, just can avoid the suction side of the second rotation compression assembly to reverse phenomenon, and cost of production also can reduce with the pressure of discharging side.
According to another embodiment of the present invention, the refrigerant pipe arrangement is used for making by the refrigerant of the first rotation compression assembly compression being inhaled into the second rotation compression assembly; Intermediate cooling loop is connected side by side with cold pipe arrangement; And control valve unit, make the cryogen flow of discharging from first rotary compressing device to refrigerant pipe arrangement or intermediate cooling loop in order to control.Therefore, can select whether to flow into intermediate cooling loop according to the state of refrigerant.
Thus, when flowing to intermediate cooling loop, can avoid the interior temperature of compressor that the shortcoming of abnormal ascending is arranged.When flowing to the refrigerant pipe arrangement, the refrigerant discharge temperature in the time of can making compressor start rises soon.The refrigerant that is immersed in the compressor class can be returned to normal state apace, and the startability of compressor is promoted.
Above-mentioned cooling circulation device more can comprise temperature detect means, is used for detecting the refrigerant temperature of discharging from the second rotation compression assembly.The discharge refrigerant temperature of the second rotation compression assembly that detects when temperature detect means is when rising to a predetermined value, and control valve unit makes cryogen flow arrive intermediate cooling loop.When lower, make cryogen flow arrive the refrigerant pipe arrangement than predetermined value.
When the discharge refrigerant temperature of the second rotation compression assembly that detects with temperature detect means is lower than predetermined value, because control valve unit makes refrigerant flow into the refrigerant pipe arrangement, when starting etc., the discharge refrigerant temperature of the second rotation compression assembly can rise very early.Thus, because refrigerant temperature can easily rise when starting, so the refrigerant that is immersed in the compressor can promptly be got back to normal state, and the startability of compressor also can further promote.
According to another embodiment of the present invention, compressor has first and second rotation compression assembly that running shaft drove that is driven assembly at seal container. is discharged in this seal container by the first rotation refrigerant that compression assembly compressed, press refrigerant gas again by the second rotation compression assembly compression in the middle of giving off. compressor comprises following formation: two cylinders constitute first and second rotation compression assembly respectively; Two rollers are separately positioned in each cylinder, and are chimeric and do eccentric rotation with the eccentric part of running shaft; Intermediate section dividing plate, position are between each cylinder and each roller, to cut apart first and second rotation compression assembly; Two supporting portion materials are sealed the respectively opening surface of this cylinder respectively, and respectively possess the bearing of this running shaft; Oilhole is formed in the running shaft; Through hole, perforation is arranged in the intermediate section dividing plate, to be communicated with the inboard of seal container inside and two rollers; The intercommunicating pore perforation is arranged in the cylinder of the second rotation compression assembly, in order to the through hole that is communicated with the intermediate section dividing plate and the suction side of the second rotation compression assembly. the through hole of intermediate section dividing plate thus, the high-pressure refrigerant that is accumulated in the roller inboard can be run away in the seal container.
Thus, utilize the pressure difference of roller inboard, oil can be supplied from the oil supply hole of running shaft smooth-goingly, so can avoid the inboard eccentric part periphery of roller to have the shortcoming of low on fuel.
In addition, even the pressure in the cylinder of the second rotation compression assembly is higher than the pressure that becomes in the middle seal container of pressing, utilization is at the suction crushing of the suction process of the second rotation compression assembly, by the through hole and the intercommunicating pore of intermediate section dividing plate, oil can positively supply to the suction side of the second rotation compression assembly from the oilhole of running shaft.Because the through hole of intermediate section dividing plate can reach that the high pressure of double as roller inboard discharges and to the fuel feeding of the second rotation compression assembly, so can reach the purpose that structure is simplified and cost reduces.
That is, utilize above-mentioned formation, the performance of rotary compressor can be guaranteed and reliability can promote.Particularly, utilization wears and is communicated with in the seal container and the through hole of roller inboard, and in the cylinder that constitutes the second rotation compression assembly, wear intercommunicating pore, with the simple structure of the suction side of the through hole that is communicated with the intermediate section dividing plate and the second rotation compression assembly etc., so the high pressure of roller inboard release and second fuel feeding that rotates compression assembly carried out.Therefore, can reach the reduction of simple structure and cost.
The revolution control type motor of driven unit in the aforesaid compressor for when starting, starting with low speed.When starting, though the second rotation compression assembly from seal container in the through hole of the intermediate section dividing plate that is communicated with suck oil the seal container, also can suppress because the bad influence that oil pressure contracts and caused, also can avoid the reliability decrease of rotary compressor.
According to another embodiment of the present invention, compressor in seal container, possess electric assembly with by rotation compression assembly that electric assembly drove.Be rotated the refrigerant that compression assembly compresses and be discharged into the outside, compressor forms reservoir in the rotation compression assembly, in order to being separated, be accumulated with the oil that refrigerant emits from the rotation compression assembly, and reservoir is communicated to seal container inside via the return path with throttling function.Therefore, the oil mass that is discharged into the rotary compressor outside from the second rotation compression assembly can reduce.
Thus, can prevent that big gauging from flowing out to the problem of the freeze cycle mis-behave that is caused in the cryogen circuit of freeze cycle.
In addition, the oil that is accumulated in reservoir is got back in the seal container with the return path with throttling function, so can avoid the shortcoming of low on fuel in the seal container.
Generally speaking, can do one's utmost to reduce in the cryogen circuit that oil is discharged into refrigerant cycle, and can smooth-going ground fuel feeding in seal container.Therefore, the performance of rotary compressor and reliability can promote.
According to another embodiment of the present invention, compressor has electric assembly and by rotary compressor structure that electric assembly drove in seal container.The rotary compressor structure is made of first and second rotation compression assembly, is discharged in the seal container by the first rotation refrigerant that compression assembly compressed, and presses refrigerant to compress with the second rotation compression assembly in the middle of emitting, and is discharged into the outside.Compressor forms reservoir in the rotary compressor structure, be separated, accumulate with the oil that refrigerant emits in order to rotating compression assembly from second, and reservoir is communicated to seal container inside via the return path with throttling function.Therefore, the oil mass that is discharged into the rotary compressor outside from the second rotation compression assembly can reduce.
Thus, can prevent that big gauging from flowing out to the problem of the freeze cycle mis-behave that is caused in the cryogen circuit of freeze cycle.
In addition, the oil that is accumulated in reservoir is got back in the seal container with the return path with throttling function, so can avoid the shortcoming of low on fuel in the seal container.
Generally speaking, can do one's utmost to reduce in the cryogen circuit that oil is discharged into refrigerant cycle, and can smooth-going ground fuel feeding in seal container.Therefore, the performance of rotary compressor and reliability can promote.
Above-mentioned compressor more comprises: second cylinder constitutes the second rotation compression assembly; First cylinder sees through the intermediate section dividing plate and is configured in second cylinder below, and in order to constitute the first rotation compression assembly; The first supporting portion material is in order to seal the below of first cylinder; The second supporting portion material is in order to seal the top of second cylinder; And the suction path, in the first rotation compression assembly.Reservoir is formed in first cylinder that sucks part beyond the path.Constitute thus, space efficiency is promoted.
In the above-mentioned compressor, reservoir utilizes up/down perforation second cylinder, intermediate section dividing plate, constitutes with the through hole of first cylinder.Therefore, can improve the processing operation that constitutes reservoir significantly.
In sum; though the present invention discloses as above with preferred embodiment; right its is not in order to limit the present invention; any person skilled in the art person; without departing from the spirit and scope of the present invention; cocoa is used for a variety of modifications and variations, so protection scope of the present invention is when looking being as the criterion that the accompanying Claim book defined.

Claims (2)

1. compressor, have by first and second rotation compression assembly that running shaft drove of a driven unit at seal container, be discharged in this seal container by this first rotation refrigerant that compression assembly compressed, press refrigerant gas again by this second rotation compression assembly compression in the middle of giving off, this compressor comprises:
Two cylinders, constitute respectively respectively this first with this second rotation compression assembly;
Two rollers are separately positioned in each cylinder, and are chimeric and do eccentric rotation with the eccentric part of this running shaft;
Intermediate section dividing plate, position first second rotate compression assembly with this to cut apart this between each cylinder and each roller;
Two supporting portion materials are sealed the respectively opening surface of this cylinder respectively, and respectively possess the bearing of this running shaft;
Oilhole is formed in this running shaft;
Through hole, perforation is arranged in this intermediate section dividing plate, to be communicated with the inboard of this seal container inside and this two roller;
Inject and use intercommunicating pore, perforation is arranged in this cylinder of this second rotation compression assembly, in order to this through hole and this second suction side that rotates compression assembly that is communicated with this intermediate section dividing plate; And
Intercommunicating pore extends and passes this intermediate section dividing plate at the upside midway of this through hole.
2. compressor as claimed in claim 1 is characterized in that: this driven unit is the revolution control type motor that starts with low speed when starting.
CN 200610056767 2002-08-30 2003-08-28 Compressor used in refrigerant cycling device Expired - Fee Related CN1818390B (en)

Applications Claiming Priority (21)

Application Number Priority Date Filing Date Title
JP2002253225 2002-08-30
JP2002-253225 2002-08-30
JP2002253225A JP2004092469A (en) 2002-08-30 2002-08-30 Rotary compressor
JP2002265542A JP2004101114A (en) 2002-09-11 2002-09-11 Transition critical refrigerant cycle apparatus
JP2002265365A JP4039921B2 (en) 2002-09-11 2002-09-11 Transcritical refrigerant cycle equipment
JP2002-265365 2002-09-11
JP2002-265542 2002-09-11
JP2002265542 2002-09-11
JP2002265365 2002-09-11
JP2002268321A JP4118109B2 (en) 2002-09-13 2002-09-13 Rotary compressor
JP2002-268321 2002-09-13
JP2002268321 2002-09-13
JP2002272986A JP4107926B2 (en) 2002-09-19 2002-09-19 Transcritical refrigerant cycle equipment
JP2002-272986 2002-09-19
JP2002272986 2002-09-19
JP2002-275172 2002-09-20
JP2002275172A JP3995570B2 (en) 2002-09-20 2002-09-20 Refrigerant circuit device
JP2002275172 2002-09-20
JP2002-283956 2002-09-27
JP2002283956 2002-09-27
JP2002283956A JP2004116957A (en) 2002-09-27 2002-09-27 Refrigerant cycle system

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
CNB031564488A Division CN100498121C (en) 2002-08-30 2003-08-28 refrigerant circulation device

Publications (2)

Publication Number Publication Date
CN1818390A CN1818390A (en) 2006-08-16
CN1818390B true CN1818390B (en) 2010-05-12

Family

ID=32264526

Family Applications (3)

Application Number Title Priority Date Filing Date
CN 200610056767 Expired - Fee Related CN1818390B (en) 2002-08-30 2003-08-28 Compressor used in refrigerant cycling device
CNB2006100567652A Expired - Fee Related CN100412465C (en) 2002-08-30 2003-08-28 Refrigerant cycling device
CNB2006100567667A Expired - Fee Related CN100370197C (en) 2002-08-30 2003-08-28 Compressor for refrigerant cycling device

Family Applications After (2)

Application Number Title Priority Date Filing Date
CNB2006100567652A Expired - Fee Related CN100412465C (en) 2002-08-30 2003-08-28 Refrigerant cycling device
CNB2006100567667A Expired - Fee Related CN100370197C (en) 2002-08-30 2003-08-28 Compressor for refrigerant cycling device

Country Status (2)

Country Link
JP (1) JP4039921B2 (en)
CN (3) CN1818390B (en)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006161659A (en) * 2004-12-07 2006-06-22 Hitachi Ltd Refrigerating cycle device
US7900468B2 (en) * 2007-07-11 2011-03-08 Liebert Corporation Method and apparatus for equalizing a pumped refrigerant system
JP5003439B2 (en) * 2007-11-30 2012-08-15 ダイキン工業株式会社 Refrigeration equipment
JP5125611B2 (en) * 2008-02-29 2013-01-23 ダイキン工業株式会社 Refrigeration equipment
CN102588291A (en) * 2011-01-11 2012-07-18 珠海格力电器股份有限公司 Spray liquid cooling device and compressor provided with same
CN102678571B (en) * 2011-03-11 2016-03-02 上海日立电器有限公司 A kind of rotor compressor pump housing cooling recirculation system
JP2012251485A (en) * 2011-06-03 2012-12-20 Fujitsu General Ltd Rotary compressor
JP5927633B2 (en) * 2012-11-06 2016-06-01 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド Air conditioner
US9194615B2 (en) 2013-04-05 2015-11-24 Marc-Andre Lesmerises CO2 cooling system and method for operating same
US11656005B2 (en) 2015-04-29 2023-05-23 Gestion Marc-André Lesmerises Inc. CO2 cooling system and method for operating same
CN104848497A (en) * 2015-06-10 2015-08-19 广东志高暖通设备股份有限公司 Air conditioner
KR102339600B1 (en) * 2017-05-26 2021-12-15 엘지전자 주식회사 Rotary compressor
CN107806410A (en) * 2017-10-10 2018-03-16 珠海凌达压缩机有限公司 Rotary compressor and air-conditioning system

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0678582A (en) * 1992-08-21 1994-03-18 Sanyo Electric Co Ltd Controlling method for operation of compressor
CN2290823Y (en) * 1997-03-03 1998-09-09 刘仕英 Automatic defrost heat pump
JPH1163694A (en) * 1997-08-21 1999-03-05 Zexel Corp Refrigeration cycle
US6189335B1 (en) * 1998-02-06 2001-02-20 Sanyo Electric Co., Ltd. Multi-stage compressing refrigeration device and refrigerator using the device
JP2001091071A (en) * 1999-09-24 2001-04-06 Sanyo Electric Co Ltd Multi-stage compression refrigerating machine
JP3469832B2 (en) * 1999-10-28 2003-11-25 三洋電機株式会社 Multi-stage compression refrigeration equipment

Also Published As

Publication number Publication date
CN100370197C (en) 2008-02-20
CN1818504A (en) 2006-08-16
CN1818390A (en) 2006-08-16
CN100412465C (en) 2008-08-20
CN1818514A (en) 2006-08-16
JP2004101107A (en) 2004-04-02
JP4039921B2 (en) 2008-01-30

Similar Documents

Publication Publication Date Title
CN100498121C (en) refrigerant circulation device
CN1818390B (en) Compressor used in refrigerant cycling device
US6568198B1 (en) Multi-stage compression refrigerating device
CN1333220C (en) Refrigerant cycle apparatus
US6931866B2 (en) Multistage compression type rotary compressor and cooling device
JP5017037B2 (en) Refrigeration cycle equipment
TW200305687A (en) Multistage rotary compressor and refrigeration circuit system
CN103821716A (en) Two-stage rotary compressor and refrigeration circulating device with same
JP2007178052A (en) Refrigerating device
EP1215450A1 (en) Multi-stage compression refrigerating device
CN1316212C (en) R4efrigerant circulation device
CN102822609A (en) Refrigeration cycle apparatus and method for operating same
CN203756524U (en) Double-level rotating compressor and refrigerating cycling device with same
CN102003390B (en) Vortex compressor
WO2015131313A1 (en) Two-stage rotary compressor and refrigerating circulation device having same
CN1816696B (en) Scroll-type fluid machine
JP2006105458A (en) Refrigerant circulation system and hermetic compressor
JP6446542B2 (en) Variable capacity compressor and refrigeration apparatus including the same
CN100498119C (en) Refrigerant cycling device
CN101158516A (en) Refrigerant cycling device
JP2001082369A (en) Two-stage compression type rotary compressor
CN1807896B (en) Multi-stage compression type rotary compressor
CN103791645B (en) Refrigerating circulatory device
CN103486751B (en) Refrigerating circulatory device
JP2012247104A (en) Refrigerating device including scroll 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
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20100512

Termination date: 20150828

EXPY Termination of patent right or utility model