CN104380009B - Refrigerant compressor and heat pump device - Google Patents
Refrigerant compressor and heat pump device Download PDFInfo
- Publication number
- CN104380009B CN104380009B CN201280073851.8A CN201280073851A CN104380009B CN 104380009 B CN104380009 B CN 104380009B CN 201280073851 A CN201280073851 A CN 201280073851A CN 104380009 B CN104380009 B CN 104380009B
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- China
- Prior art keywords
- discharge
- compression mechanism
- oil
- hermetic container
- discharge path
- 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.)
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Classifications
-
- 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
- F25B31/00—Compressor arrangements
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/04—Heating; Cooling; Heat insulation
-
- 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
- F04C2240/00—Components
- F04C2240/80—Other components
- F04C2240/809—Lubricant sump
-
- 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
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/05—Compression system with heat exchange between particular parts of the system
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/16—Lubrication
Abstract
This refrigerant compressor (110) comprises an airtight container (8), a compression mechanism (3) accommodated in the airtight container (8) and used for drawing in and compressing refrigerant, an electric motor (9) accommodated in the airtight container (8) and used for driving the compression mechanism (3), and an oil storage part (50) formed in the bottom part of the airtight container (8) and used for storing lubricating oil; the interior of the airtight container (8) being an atmosphere of refrigerant intake pressure, and the interior of the airtight shell being provided with a heat exchange means for heating using high-pressure refrigerant immediately after the lubricating oil stored in the oil storage part (50) has been discharged from the compression mechanism (3).
Description
Technical field
The present invention relates to coolant compressor and heat pump assembly, more particularly in fridge-freezer, air conditioner or hot water
Coolant compressor and the heat pump assembly using the compressor used in the heat pump assemblies such as supply machine.
Background technology
In recent years, in coolant compressor, from from the viewpoint of seeking to prevent global warming, need the fluorine profit to using
Technology that high refrigerant amount is cut down, the use of depletion of the ozone layer coefficient is the little combustible refrigerant of zero, global warming coefficient
Technology.
Particularly the superior hydrocarbon refrigerant of refrigerant property (hereinafter referred to as " HC cold-producing mediums ") is expected.HC freezes
Agent, from sliding part greasy property, from the viewpoint of spilling sealing property, theory COP, possesses the system equal with freon refrigerant
Cryogen characteristic, has used the fridge-freezer of iso-butane to produce in batches, but from the danger of combustible refrigerant, system
Cryogen allows that charging quantity is limited by international standard.For example, according to IEC standard, needs can will be filled in home-use air conditioner
Within hydrocarbon refrigerant amount is cut to about 150g.
Accordingly, as the means that cold-producing medium allows the restriction of charging quantity are solved, herein below is reported, i.e. PAG (poly- Asias
Alkyl diol) it is low with the intermiscibility of HC cold-producing mediums (R290), by PAG is used as lubricating oil, refrigerant charge amount can be reduced
(no longer need the meltage predicted in lubricating oil and extraly enclose refrigerant amount) (for example, referring to non-patent literature 1).
In addition, an invention is disclosed, in the invention, by using oil (the non-phase low with the intermiscibility of HC cold-producing mediums
Molten oiling) as lubricating oil, also, make the interior cold-producing medium that becomes of closed shell (hermetic container) of storage lubricating oil suck pressure ring border
(low-pressure shell), reduces meltage of the HC cold-producing mediums relative to lubricating oil (for example, referring to patent documentation 1).
In addition, there is also an issue, i.e. if using the lubricating oil relative to HC cold-producing mediums with non-compatibility property,
The lubricating oil being carried in freeze cycle fully can not be returned in compressor.In order to solve this problem, one is disclosed
Item invention, the invention adopt High Pressure Shell type compressor or middle die mould compressor, diffluent using having HC cold-producing mediums to hold
The paraffin mineral oil of property is heated to the lubricating oil in compressor in being arranged on the operating of compressor as lubricating oil
Heating arrangements, make the refrigerant amount being dissolved in lubricating oil reduce (for example, referring to patent documentation 2).
Prior art literature
Patent documentation
Patent documentation 1：Japanese Unexamined Patent Publication 8-200224 publication (the 2-3 page, Fig. 1)
Patent documentation 2：Japanese Unexamined Patent Publication 11-294877 publication (the 3-4 page, Fig. 3)
Non-patent literature
Non-patent literature 1：High bridge core " characteristic of cold-producing medium/refrigerator oil mixture ", Japan Refrigeration and Air Conditioning Industry Association
Sponsor, the 160-164 page of alternative refrigerant and 2002 collection of thesis of environment international symposium
The content of the invention
Invent problem to be solved
However, in patent documentation 1, although disclose in reduction cold-producing medium in terms of the meltage in lubricating oil, non-phase
Molten oiling and low-pressure shell are effective means, but do not account for inventor etc. as the middle discovery such as following test evaluations
, by the lubricating oil caused by the change of the operating condition in the compressor of low-pressure shell form dynamic viscosity change greatly
It is little.
In addition, patent documentation 2 is also only the compressor for describing High Pressure Shell or intermediate pressure form, low pressure shell is not accounted for
Body.
Then, with regard to the compressor of low-pressure shell form, by carrying out Performance comparision with the compressor of High Pressure Shell form
Following test evaluations etc., such problem becomes clear and definite below.
(experimental condition)
Inventor etc. for the new problem for proposing to be brought by low-pressure shell and non-compatibility oiling, using R290 as HC
Cold-producing medium, implements the performance of the low-pressure shell type Rotary Compressor and High Pressure Shell type Rotary Compressor of 1.5 horse power grades
Test.
Figure 11 is the figure of the condition (hereinafter referred to as " compressor experimental condition ") for arranging such performance test, with regard to (a)
ASHRAE-T conditions, (b) specified refrigeration test condition, refrigeration test condition in the middle of (c), (d) is specified heats experimental condition, (e)
Centre heats 7 conditions difference realities that experimental condition, (f) Europe hot water supply heat A2W35 conditions and (g) China GB conditions
Apply.
Now, viscometer (Cambridge company online viscometer 1600) is installed on compressor housing bottom, is made using R290
For HC cold-producing mediums, with regard to the high naphthene series mineral oil (NM100) of the intermiscibility as lubricating oil and the intermiscibility containing EO50% is low
PAG oil 2 levels, determine oily dynamic viscosity during each operating.
(R290 and naphthene series mineral oil)
Figure 12 is as HC cold-producing mediums, using the high naphthene series mineral oil (NM100) of intermiscibility as lubrication using R290
Oil, implements the measurement result in the case of above-mentioned each test, represents the dynamic viscosity change of the lubricating oil.
As shown in Figure 12, in the case of low-pressure shell type compressor, compared with High Pressure Shell type compressor, oil
Dynamic viscosity is high, such as about 5 times are reached during specified heating operation, and mechanical loss becomes very large.Also, oily dynamic viscosity changes
Amplitude is also big, and maximum (during specified heating operation condition) reaches about 7 with the ratio of minima (during middle cooling operation condition)
Times, it is therefore difficult to be taken into account the design that bearing durability guarantees to reduce with mechanical loss over a wide range of conditions.
So used in low-pressure shell type compressor HC cold-producing mediums, using mineral such as the high naphthene series mineral oil of intermiscibility
In the case that oil is as lubricating oil, learn there is problems with, i.e. oily dynamic viscosity amplitude of fluctuation is big, it is difficult to carry out in wide model
Take into account under conditions of enclosing bearing durability guarantee (wish that viscosity is big) and mechanical loss reduce (wishing that viscosity is little) design.
(R290 and PAG oil)
It (here, using viscosity is VG22 into the low PAG oil of intermiscibility containing EO50% by oil change that Figure 13 is
The PAG oil) result of same test is implemented, represent the dynamic viscosity change of the lubricating oil.
As shown in Figure 13, in the case of low-pressure shell type compressor, compared with High Pressure Shell type compressor, oil
Dynamic viscosity is about 2.5 times in specified heating operation, in addition, maximum (the middle system as oily dynamic viscosity amplitude of fluctuation
During heat test condition) it is about 2 times with the ratio of minima (middle refrigeration test condition).
So used in low-pressure shell type compressor HC cold-producing mediums, using the low PAG oil of intermiscibility as lubricating oil
In the case of, oily dynamic viscosity amplitude of fluctuation is with being diminished compared with the situation of lubricating oil using mineral oil such as naphthene series mineral oil.
In addition, with regard to HC cold-producing mediums and the dissolubility of PAG oil, showing that in non-patent literature 1 R290 (propane) freezes
The solubility curve of agent and main lubricating oil (mineral oil, POE oil, PAG oil), from these solubility curves it is known that alkane
Base glycol (PAG) oil phase is low for the intermiscibility of HC cold-producing mediums, the oil phase ratio with the intermiscibility such as mineral oil, cold-producing medium dissolubility
Change is little, can cut down HC cold-producing medium enclosed volumes.
By being used as lubricating oil relative to the low PAG oil of the intermiscibility of HC cold-producing mediums so used in low-pressure shell, with
Compared using mineral oil as the situation of lubricating oil, oily dynamic viscosity amplitude of fluctuation can be reduced, in addition, passing through non-compatibility oiling
And low-pressure shellization can reduce meltage (can reduce refrigerant charge amount) of the HC cold-producing mediums in lubricating oil.
However, from from the viewpoint of guaranteeing to take into account the degree of freedom that bearing durability is guaranteed with the design of mechanical loss reduction,
Need further to reduce the oily dynamic viscosity amplitude of fluctuation of PAG.
In addition, if increasing EO (oxirane) amount in PAG oil, then the phase relative to HC cold-producing mediums can be reduced
Dissolubility (can reduce refrigerant charge amount), but thus produce the reduction of lubricated sliding wear performance, produce when particularly more than 50%
The problem that lubricated sliding wear performance is drastically reduced.Accordingly, as to the reduction of lubricated sliding wear performance caused by increase EO amounts
Countermeasure, needs certain means being controlled to the oily dynamic viscosity of PAG.
In addition, if reduce the mean molecule quantity in PAG oil, then the viscosity of the state that can debase the standard, but then,
Volatility is uprised, and burning-point is reduced.Under VG18 (ISO viscosity criterions), burning-point is 183 DEG C, and VG18 is to make in actual applications
The limit of viscosity.From the limit that the viscosity of the standard state of such PAG oil is reduced, it is also desirable to which the oil of PAG is moved
Certain means that power viscosity is controlled.
(excursion of cold-producing medium dissolubility)
Figure 14 is in the case of low-pressure shell type and to compare relative to temperature and pressure in the case of High Pressure Shell type
Cold-producing medium dissolubility excursion figure.
Figure 15 be in the case of low-pressure shell type and High Pressure Shell type in the case of compare cold-producing medium dissolve when oil
The figure of the excursion of dynamic viscosity.
Usually, as shown in Figure 14, the curve chart that the relation of cold-producing medium dissolubility and pressure is indicated is closed
When variant temperature conditionss represent pressure 0, cold-producing medium dissolubility becomes 0 loaarithmic curve.That is, make storage lubricating oil
In the case of discharging the High Pressure Shell type in pressure ring border in closed shell (hermetic container) for cold-producing medium, if the discharge pressure of compressor
Condition changes, then the pressure, temperature variation of the oil being stored in closed shell (hermetic container).On the other hand, in low-pressure shell
In the case of type, if the suction press strip part change of compressor, the pressure of the oil being stored in closed shell (hermetic container)
And temperature change.
From in terms of the characteristic of the cold-producing medium solubility curve that can be represented with loaarithmic curve as Figure 14, in low-temp low-pressure
Side, compared with High Pressure Shell type, the impact applied to cold-producing medium dissolubility is bigger for the low-pressure shell type of pressure, temperature variation, system
Cryogen changes in solubility is also bigger.As a result, as shown in Figure 15, oily dynamic viscosity excursion is also in low-pressure shell type
Middle ratio is bigger in High Pressure Shell type.
As described above, in order to tackle low-pressure shell and non-compatibility oiling, propose following such new problem.
(1) as the means of the cold-producing medium dissolubility for reducing HC cold-producing mediums, although the use of the PAG oil of non-compatibility property is effective
, but PAG oil is actually unable in the low oil of manufacture ratio of viscosities VG18.Therefore, in order that design bearing is suitably changed, reduces machinery damage
Lose, need the other means being controlled to the physical property of PAG oil.
(2) also, in the case of using low-pressure shell form, the system of the oil being stored in closed shell (hermetic container)
Cryogen dissolubility and dynamic viscosity are easily varied.Therefore, in order that design bearing is suitably changed, reduces mechanical loss, need to oil
The new means that physical property is controlled.
The present invention is made to solve problem as described above, its object is to obtain a kind of refrigerant compression
Machine and heat pump assembly, the coolant compressor and heat pump assembly can reduce cold-producing medium in the compressor of low-pressure shell form
Dissolubility in oil, cuts down cold-producing medium enclosed volume, further, it is possible to improve compressor efficiency.
Means for solving the problems
The coolant compressor of the present invention is characterised by：It is hermetic container with low-pressure shell type, compression mechanism, electronic
Machine, oil stock portion, heat exchange mechanism and multiple discharge paths；
The compression mechanism is accommodated in the hermetic container, is sucked and compression refrigerant；
The motor is accommodated in the hermetic container, and the compression mechanism is driven；
The oil stock portion is formed in the bottom in the hermetic container, and lubricating oil is stored；
The heat exchange mechanism is being stored in the lubricating oil and the refrigeration discharged from the compression mechanism in the oil stock portion
Heat exchange is carried out between agent；
The plurality of discharge path by cold-producing medium from the compression mechanism to the hermetic container outside guide；
The discharge path possesses the 1st discharge path and the 2nd discharge path, and the 1st discharge path is in the hermetic container
Inside possesses the heat exchange mechanism, the 2nd discharge path is by the cold-producing medium not with the lubricating oil with carrying out heat exchange to institute
State, the 1st discharge path is converged with the 2nd discharge path outside the hermetic container.
The effect of invention
In the present invention, because the heat energy that the high-pressure refrigerant discharged from compression mechanism has is handed over to be stored at oily storage
Lubricating oil in the portion of Tibetan, thus it is possible to reduce dissolubility in the oil of cold-producing medium, cuts down cold-producing medium enclosed volume therefore, it is possible to obtain
Effect and improve the effect of compressor efficiency and heat pump efficiency.
Description of the drawings
Fig. 1 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 1.
Fig. 2 is the structure chart of the heat pump assembly for illustrating schematically that embodiments of the present invention 2.
Fig. 3 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 3.
Fig. 4 is the structure chart of the heat pump assembly for illustrating schematically that embodiments of the present invention 4.
Fig. 5 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 5.
Fig. 6 is the structure chart of the heat pump assembly for illustrating schematically that embodiments of the present invention 6.
Fig. 7 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 7.
Fig. 8 is the structure chart of the heat pump assembly for illustrating schematically that embodiments of the present invention 8.
Fig. 9 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 9.
Figure 10 is the structure chart of the heat pump assembly for illustrating schematically that embodiments of the present invention 10.
Figure 11 is the condition of the performance test of low-pressure shell type and High Pressure Shell type.
Figure 12 is as the measurement result in the case of lubricating oil using R290 and naphthene series mineral oil.
Figure 13 is as the measurement result in the case of lubricating oil using R290 and PAG oil.
Figure 14 is the measurement result of the change for representing the cold-producing medium dissolubility relative to temperature and pressure.
Figure 15 is the measurement result for representing cold-producing medium dissolubility and the relation of oily dynamic viscosity.
Specific embodiment
[embodiment 1]
Fig. 1 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 1.In addition, each position
It is the position for schematically depicting, the present invention is not limited to the form for illustrating.
(2 cylinder compressor of low-pressure shell type)
In FIG, coolant compressor (hereinafter referred to as " 2 cylinder compressor of low-pressure shell type " or " coolant compressor ")
110 have hermetic container 8, the motor 9 being arranged in hermetic container 8, the drive shaft 6 driven by motor 9, respectively to driving
Short axle side bearing 7a and major axis side bearing 7b, the 1st (downside) being made up of the 1st (downside) cylinder 11 that the two ends of axle 6 are supported
Compression mechanism 10, the 2nd (upside) compression mechanism 20 being made up of the 2nd (upside) cylinder 21, and to the 1st (downside) cylinder the 11 and the 2nd (on
Side) intermediate plate 5 that is separated of cylinder 21.
The cold-producing medium of low pressure is inhaled in hermetic container 8 from compressor suction tube 1, is moved in hermetic container 8, by from
The 1st (downside) cylinder suction tube 15 being arranged in hermetic container 8 is attracted to the 1st (downside) cylinder of the 1st (downside) compression mechanism 10
In discharge chambe 11a, also, the 2nd (upside) of the 2nd (upside) compression mechanism 20 is attracted to from the 2nd (upside) cylinder suction tube 25
In cylinder discharge chambe 21a.
Then, the refrigeration being compressed by the 1st (downside) cylinder discharge chambe 11a and the 2nd (upside) cylinder discharge chambe 21a respectively
Agent (hereinafter referred to as " high-pressure refrigerant "), is discharged to the 1st from the 1st (downside) outlet 17 and the 2nd (upside) outlet 27 respectively
(downside) is discharged muffler space 32 and the 2nd (upside) and is discharged in muffler space 42, respectively with to the refrigeration outside hermetic container 8
The 1st (downside) discharge duct 35 that agent loop (not shown) guides is connected with the 2nd (upside) discharge duct 45.In addition, the 1st (under
Side) discharge muffler space 32 formed by container 33, by both merge be referred to as the 1st (downside) discharge acoustic filter 31.
In the 1st (downside) discharge duct 35 and the 2nd (upside) discharge duct 45, it is respectively arranged with as flow path resistance
1st valve 37 and the 2nd valve 47 of the flow path resistance mechanism being adjusted, by being adjusted to respective aperture, suitably adjusts
The refrigerant flow for flowing in the 1st (downside) discharge duct 35 and the 2nd (upside) discharge duct 45 respectively.
In addition, the 1st (downside) discharge duct 35 is closed via being arranged on from the 1st (downside) discharge muffler space 32
After the heat exchange mechanism 36 in oil stock portion 50 in container 8, guided to the outside of hermetic container 8.
In the structure of embodiments of the present invention 1, the height that 2 compression cylinders 11,21 are discharged from outlet 17,27 respectively
Compression refrigerant is constituted as described above to the discharge path 30,40 that radiator 102 (with reference to Fig. 2) is guided.Wherein, will be closed
The discharge path heated to lubricating oil in container is defined as the 1st.
In vertical compressor, as lubricating oil is stored in the bottom in hermetic container 8, so, general structure is
The discharge path for being configured at downside is named as into the 1st, the discharge path for being configured at upside is named as into the 2nd.However, also adopting sometimes
Use following structure, i.e. by the discharge path that heat exchange is energetically carried out in closed shell be named as the 1st, the 1st discharge path with
2nd discharge path is compared and is arranged as opposed in upside.
Heat exchange mechanism 36 is configured near the suction inlet of oil rotary pump 51 of the lower end for being installed on drive shaft 6, in heat friendship
The oily of flowing for being configured to block between the outside wall portions of converting mechanism 36 and hermetic container 8 lubricating oil surrounds mechanism 55, seeks absolutely
Heat.The heat-transfer pipe of for example flowed by cold-producing medium 1 or more than 2 of heat exchange mechanism 36 and it is arranged on many on the heat-transfer pipe
Individual heat sink (fin) is constituted, and is submerged in lubricating oil.
Discharge muffler space 32 and connected by stream 46 is connected with the 2nd (upside) discharge muffler space 42 in 1st (downside).
In addition, connecting stream 46 insertion the 1st (downside) cylinder 11, the 2nd (upside) cylinder 21 and intermediate plate 5 in the axial direction.In addition, the 2nd (on
Side) discharge muffler space 42 formed by container 43, by both merge be referred to as top discharge acoustic filter 41.
For example, at low ambient conditions, there are the following problems, i.e. because inlet temperature is reduced, is stored in hermetic container
In oil temperature reduce, oil viscosity increases, and the mechanical loss of compressor increases.
In embodiments of the present invention 1, throttled by making the 2nd valve 47, the 1st valve 37 is opened, pressed by the 1st compression cylinder 11
Contracting, the high-pressure refrigerant being discharged to from the 1st outlet 17 in the 1st discharge muffler space 32, by connecting stream 46 to the 2nd row
Go out muffler space 42 to flow, thus it is possible to the flow for making to flow through the 2nd (upside) discharge duct 45 is reduced, make to flow through the 1st (under
Side) discharge duct 35 flow increase.That is, because the oil by heat exchange mechanism 36 flow increase, therefore, by with oil
Heat exchange amount (the reception amount of heat energy) increases, and oil temperature rises, and obtains the effect that oil viscosity is reduced.
From the description above, 2 cylinder compressor 110 of low-pressure shell type of embodiment 1 can be controlled to oil temperature, because
This, in the oil of cold-producing medium, dissolubility and oily dynamic viscosity amplitude of fluctuation diminish, and obtain and cut down the effect of cold-producing medium enclosed volume and make
The effect that compressor efficiency is improved.
In addition, because being placed between the wall of heat exchange mechanism 36 and hermetic container 8 for blocking the stream of lubricating oil
Dynamic oil surrounds mechanism 55, so, the inside of mechanism 55 is surrounded in oil, heat lubricating oil, prevent heat energy to the outer of hermetic container 8
The dissipation in face.
In addition, as lubricating oil, use the lubricating oil little with the intermiscibility of hydrocarbon refrigerant, for example, using containing epoxy
The alkyl diol of ethane, so that the dynamic viscosity under 40 DEG C, atmospheric pressure is in more than 18cSt.
[embodiment 2]
Fig. 2 is the structure chart of the partial longitudinal section of the heat pump assembly for illustrating schematically that embodiments of the present invention 2.In addition,
With 1 identical part of embodiment, mark same reference, clipped explanation.In addition, each position is
The position for schematically depicting, the present invention are not limited to the form for illustrating.
(Teat pump hot water supply device)
In fig. 2, heat pump assembly (hereinafter referred to as " Teat pump hot water supply device ") 140 possesses main refrigerant circuit 120 and profit
With fluid circuit 130.Main refrigerant circuit 120, by coolant compressor 110, radiator 102, expansion valve 103, vaporizer
104th, linking them successively makes the refrigerant piping 105 of refrigerant cycle to realize freeze cycle.
Here, coolant compressor 110 is 2 cylinder compressor the 110, the 1st of low-pressure shell type illustrated in embodiment 1
(downside) discharge duct 35 and the 2nd (upside) discharge duct 45 are respectively in the 1st valve 37 and the downstream (hermetic container 8 of the 2nd valve 47
Outside) converge.
And, in radiator 102, by make cold-producing medium (high-pressure refrigerant) that coolant compressor 110 have compressed with
Flowing through carries out heat exchange using the utilization fluid (being water here) of fluid circuit 130, and cold-producing medium is transferred heat energy and is cooled, profit
Heat energy is received with fluid and is heated.That is, the utilization being heated in radiator 102 using 130 effectively utilizes of fluid circuit
Fluid.
Now, in Teat pump hot water supply device 140, need to discharge formed high-boiling operating by high temperature.In this feelings
Under condition, by closing the 1st valve 37, the 2nd valve 47 is opened, increase can the flow that flowed in the 2nd (upside) discharge duct 45.
That is, can will be supplied to radiator 102 without the high temperature refrigerant for heat exchange being carried out with oil.
On the other hand, in the case where height output is needed with normal leaving water temperature, because coolant compressor 110 is with height
Rotating speed carry out action, there is the big pressure loss in discharge unit, so, in order to reduce the pressure loss, make the 1st valve 37 and the 2nd
The ground action of 47 standard-sized sheet of valve.
Also, in order to reduce noise by produced by pressure fluctuation, vibration, by making to discharge acoustic filter in the 1st (downside)
Discharge mutual via stream 46 is connected with the pressure fluctuation of antiphase generation between muffler space 42 with the 2nd (upside) in space 32
Propagate on ground, it is possible to obtain reduce the effect of the amplitude of pressure fluctuation.
In addition, the control of the aperture of the 1st valve 37 and the 2nd valve 47, oil temperature simultaneously in detection hermetic container 8, hermetic container 8
Outside wall temperature or discharge temperature, be controlled simultaneously actively, or according to purposes, environmental condition, be adjusted to fifty-fifty efficiency
Highest aperture.
From the description above, the Teat pump hot water supply device 140 of embodiment 2 has 2 cylinder of low-pressure shell type of embodiment 1
Compressor 110, thus it is possible to reduce dissolubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium, acquisition improves heat pump effect
The effect of rate.
[embodiment 3]
Fig. 3 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 3.In addition, with enforcement
1 identical part of mode, marks same reference, clipped explanation.In addition, each position is schematically to retouch
The position painted, the present invention are not limited to the form for illustrating.
(2 cylinder compressor of low-pressure shell type)
In figure 3, coolant compressor (hereinafter referred to as " 2 cylinder compressor of low-pressure shell type ") 210 is provided with oil and returns back
Road 56.The oily return loop 56, in the side from the 1st (downside) discharge duct 35 and the 2nd (upside) discharge duct 45 or
The cold-producing medium that two sides are flowed out carried out in refrigerant loop (not shown) it is separating of oil after, the oil for having been separated is returned to into the
In 1 (downside) compression mechanism 10 and the 2nd (upside) compression mechanism 20.
That is, in 2 cylinder compressor 210 of low-pressure shell type, with 2 cylinder compressor 110 of low-pressure shell type shown in embodiment 1
Similarly, muffler space 32 is discharged via be arranged on hermetic container 8 from the 1st (downside) in the 1st (downside) discharge duct 35
After heat exchange mechanism 36 in interior oil stock portion 50, the outside of hermetic container 8 is directed to, is lubricated in heat exchange mechanism 36
Oil is heated, so, the effect for cutting down cold-producing medium enclosed volume and the effect for improving compressor efficiency can be obtained.
Also, it is adjusted by the aperture to the 1st valve 37 and the 2nd valve 47, is suitably adjusted respectively in the 1st discharge duct
The refrigerant flow flowed in 35 and the 2nd discharge duct 45, so, in order to reduce the pressure loss in discharge duct, can be with
Valve 37,47 standard-sized sheets are made, another aspect is needing heat exchange amount of the increase with oil, making oily dynamic viscosity reduction, cold-producing medium dissolubility
In the case of reduction, can enter to exercise 37 standard-sized sheet of the 1st valve, close the adjustment such as the 2nd valve 47, the reduction and compression to cold-producing medium enclosed volume
The improvement of engine efficiency is effective.
Now, in order to obtain by valve 37,47 be opened and closed adjust adjust with oil heat exchange amount function, can match somebody with somebody
Put connection stream 46 so that the cold-producing medium from compression cylinder discharge is before the heat exchange mechanism 36 via the 1st discharge path side 35
Can converge with the 2nd discharge path.
[embodiment 4]
Fig. 4 is the structure chart of the partial longitudinal section of the heat pump assembly for illustrating schematically that embodiments of the present invention 4.In addition,
With 3 identical part of embodiment, mark same reference, clipped explanation.In addition, each position is
The position for schematically depicting, the present invention are not limited to the form for illustrating.
(Teat pump hot water supply device)
In the diagram, heat pump assembly 240 possesses by compressor 210, radiator 102, expansion valve 103,104 and of vaporizer
Linking them successively makes the refrigerant piping 105 of refrigerant cycle to realize the main refrigerant circuit 220 of freeze cycle.Now,
Oil eliminator 57 is set between compressor 210 and radiator 102.
And, the 1st (downside) discharge duct 35 and the 2nd (upside) discharge duct 45 are in the 1st valve 37 and the downstream of the 2nd valve
(outside of hermetic container 8) is converged, and is temporarily directed in oil eliminator 57, it is separating of oil after cold-producing medium by radiator 102
Guiding.On the other hand, the oil for having been separated, is pressed to the 1st (downside) compression mechanism 10 and the 2nd (upside) by oily return loop 56
Contracting mechanism 20 supplies (return).
From the description above, the heat pump assembly 240 of embodiment 4 has 2 cylinder compressor of low-pressure shell type of embodiment 1
110, thus it is possible to reduce dissolubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium, acquisition improves the effect of heat pump efficiency
Really.In addition, also can be according to the Teat pump hot water supply device 140 shown in embodiment 2, will be using fluid circuit 130 and radiator 102
Carry out thermally coupled.
[embodiment 5]
Fig. 5 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 5.In addition, with enforcement
1 identical part of mode, marks same reference, clipped explanation.In addition, each position is schematically to retouch
The position painted, the present invention are not limited to the form for illustrating.
(2 cylinder compressor of low-pressure shell type)
In Figure 5, coolant compressor (hereinafter referred to as " 2 cylinder compressor of low-pressure shell type ") 310, is provided with will be via
After the low pressure refrigerant that compressor suction tube 1 is directed in hermetic container 8 is temporarily directed to the outside of hermetic container 8, to the 1st
(downside) cylinder discharge chambe 11a guiding the 1st (downside) cylinder suction tube 15 and to the 2nd (upside) cylinder discharge chambe 21a guiding the 2nd
(upside) cylinder suction tube 25.Therefore, in the purposes based on the cooling of fridge-freezer, refrigerating plant etc., inhale with reducing
Enter the effect of loss on heating, it is superior compared with shown by embodiment 1.
In addition, making the 1st (downside) that the pressure fluctuation of the firm discharge from the 1st (downside) compression mechanism 10 decays in composition
Multiple fins 38 that heat transmission is set on the container 33 of acoustic filter 31 are discharged, and radiating itself are not provided with the 1st discharge path 35
Fin.Therefore, with using independent heat exchanger (structure of the fin of heat transmission is arranged in the 1st discharge path 35 itself)
Compare, it is favourable in terms of cost degradation and densification.
That is, in 2 cylinder compressor 310 of low-pressure shell type, by discharging muffler space 32 and fin from the 1st (downside)
38 heat transfer, lubricating oil are heated, so, the effect for cutting down cold-producing medium enclosed volume and the effect for improving compressor efficiency can be obtained
Really.
Also, it is adjusted by the aperture to the 1st valve 37 and the 2nd valve 47, is suitably adjusted respectively in the 1st discharge duct
The refrigerant flow flowed in 35 and the 2nd discharge duct 45, so, in order to reduce the pressure loss in discharge duct, can make
Valve 37,47 standard-sized sheets, on the other hand, are needing heat exchange amount of the increase with oil, are subtracting oily dynamic viscosity reduction, cold-producing medium dissolubility
In the case of little, can enter to exercise 37 standard-sized sheet of the 1st valve, close the adjustment such as the 2nd valve 47, the reduction and compressor to cold-producing medium enclosed volume
The improvement of efficiency is effective.
[embodiment 6]
Fig. 6 is the structure chart of the partial longitudinal section of the heat pump assembly for illustrating schematically that embodiments of the present invention 6.In addition,
With 5 identical part of embodiment, mark same reference, clipped explanation.In addition, each position is
The position for schematically depicting, the present invention are not limited to the form for illustrating.
(Teat pump hot water supply device)
In figure 6, heat pump assembly 340 possesses by compressor 310, radiator 102, expansion valve 103,104 and of vaporizer
Linking them successively makes the refrigerant piping 105 of refrigerant cycle to realize the main refrigerant circuit 320 of freeze cycle.
Therefore, heat pump assembly 340 has the coolant compressor 310 of embodiment 5, can reduce molten in the oil of cold-producing medium
Xie Du and oily dynamic viscosity amplitude of fluctuation, so, can obtain improves the effect of heat pump efficiency.In addition, also can be according to embodiment 2
Shown Teat pump hot water supply device 140, will carry out thermally coupled using fluid circuit 130 and radiator 102.
[embodiment 7]
Fig. 7 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 7.In addition, with enforcement
5 identical part of mode, marks same reference, clipped explanation.In addition, each position is schematically to retouch
The position painted, the present invention are not limited to the form for illustrating.
(1 cylinder compressor of low-pressure shell type)
2 cylinder compressor 310 of low-pressure shell type shown in embodiment 5 is by the 1st (downside) compression mechanism 10 and the 2nd (upside)
Compression mechanism 20 this 2 compression mechanisms are constituted, but in the figure 7, coolant compressor 410 be compression mechanism be made up of 1 cylinder it is low
1 cylinder compressor of pressure shell build, this is its difference.
Cylinder suction tube 65 is provided with 1 cylinder compressor 410 of this low-pressure shell type.Cylinder suction tube 65, will be via compressor
After the low pressure refrigerant that suction tube 1 is directed in hermetic container 8 is temporarily directed to the outside of hermetic container 8, to cylinder discharge chambe 61a
Guiding.Therefore, in the purposes based on the cooling of fridge-freezer, refrigerating plant etc., loss on heating is sucked with reducing
Effect is superior compared with shown by embodiment 1.
In embodiments of the present invention 7, even if the connection stream 46 not having as embodiment 1 to 6, also because cylinder
2 outlets 27,17 of discharge chambe 61a are dividually installed up and down, so, even if not connecting stream, by making the 2nd valve 47
Throttle, the 1st valve 37 is opened, the high-pressure refrigerant being compressed by the 1st compression cylinder 61 also becomes easily from cylinder discharge chambe 61a
Flow to the 2nd discharge muffler space 42, thus it is possible to reduce the flow flowed in the 2nd (upside) discharge duct 45, make
The flow flowed in the 1st (downside) discharge duct 35 increases.That is, increased by the flow of the oil of heat exchange mechanism 36, so,
By increasing with the heat exchange amount (the reception amount of heat energy) of oil, the effect that oil temperature rises, oil viscosity is reduced can be obtained.
In addition, though hermetic container base 90 is provided with the bottom surface of the hermetic container 8 of coolant compressor 410, but
The form of hermetic container base 90 is not limited to the form for illustrating.In addition, in other embodiments 1～6, also similarly can set
Put hermetic container base 90.
It is the structure same with embodiment 1 in addition, in 1 cylinder compressor 410 of low-pressure shell type, by the 1st
The aperture of valve 37 and the 2nd valve 47 is adjusted, and suitably adjusts and flows in the 1st discharge duct 35 and the 2nd discharge duct 45 respectively
Dynamic refrigerant flow, can obtain the effect for cutting down cold-producing medium enclosed volume and the effect for improving compressor efficiency.
[embodiment 8]
Fig. 8 is the structure chart of the partial longitudinal section of the heat pump assembly for illustrating schematically that embodiments of the present invention 8.In addition,
With 7 identical part of embodiment, mark same reference, clipped explanation.In addition, each position is
The position for schematically depicting, the present invention are not limited to the form for illustrating.
(Teat pump hot water supply device)
In fig. 8, heat pump assembly 440 possesses by compressor 410, radiator 102, expansion valve 103,104 and of vaporizer
Linking them successively makes the refrigerant piping 105 of refrigerant cycle to realize the main refrigerant circuit 120 of freeze cycle.
Therefore, because heat pump assembly 440 has the coolant compressor 410 of embodiment 7, therefore, it is possible to reduce refrigeration
Dissolubility and oily dynamic viscosity amplitude of fluctuation in the oil of agent, acquisition improve the effect of heat pump efficiency.In addition, also can be according to embodiment party
Teat pump hot water supply device 140 shown in formula 2, will carry out thermally coupled using fluid circuit 130 and radiator 102.
[embodiment 9]
Fig. 9 is the longitudinal section of the coolant compressor for illustrating schematically that embodiments of the present invention 9.In addition, with enforcement
7 identical part of mode, marks same reference, clipped explanation.In addition, each position is schematically to retouch
The position painted, the present invention are not limited to the form for illustrating.
(1 cylinder compressor of low-pressure shell type：It is horizontal)
More than, by embodiment 1～7 represent as vertical compressor in, due to lubricating oil be stored in it is closed
Bottom in container 8, so, the 1st discharge path heated to lubricating oil in hermetic container 8 will be configured at downside
Discharge path is named as the 1st, the discharge path for being configured at upside is named as the 2nd features simple structure, but will be in hermetic container 8
The discharge path for energetically carrying out heat exchange is named as the 1st, can also be sometimes be arranged as opposed to compared with the 2nd discharge path in
The structure of upside.
In fig .9, the coolant compressor 510 shown in present embodiment 9, and makes the cold-producing medium pressure shown in embodiment 7
The compressor that contracting machine (1 cylinder compressor of low-pressure shell type) 410 becomes horizontal is suitable.
In coolant compressor (1 cylinder compressor of low-pressure shell type) 510, support in 9 side of motor to drive shaft 6
Major axis side bearing 7b sides formed from cylinder discharge chambe 61a discharge high-pressure refrigerant the 1st outlet the 77, the 1st discharge acoustic filter 71,
Muffler space 72 is discharged with the 1st, the fin promoted with the heat exchange of oil is set on the 1st surface for discharging acoustic filter container 73
78.It is provided with from the 1st the 1st discharge duct 75 that guides to radiator 102 of discharge muffler space 72 and to the 1st discharge duct 75
The valve 77 that is adjusted of aperture.
On the other hand, in short axle side bearing 7a sides, form the 2nd outlet the 87, the 2nd and discharge the discharge noise elimination of acoustic filter the 81, the 2nd
Device space 82, is provided with from the 2nd the 2nd discharge duct 85 that guide to radiator 102 of discharge muffler space 72 and to the 2nd discharge
The valve 87 that the aperture of stream 85 is adjusted.It is adjusted by the aperture to the 1st valve 77 and the 2nd valve 87, suitably adjustment point
The refrigerant flow not flowed in the 1st discharge duct 75 and the 2nd discharge duct 85.
In addition, the end of a side of fuel feed pump 52 is connected with the short axle side bearing 7a sides of drive shaft 6, fuel feed pump 52 it is another
The end of side is located at oil stock portion 50.In addition, arranging hermetic container base 90 in the side (cylindrical portion) of hermetic container 8.
Coolant compressor 510, in addition to the foregoing, is the knot same with coolant compressor 410 (embodiment 7)
Structure, because being heated to lubricating oil by the heat transfer from the 1st discharge muffler space 72 and fin 78, can obtain
The effect for cutting down cold-producing medium enclosed volume and the effect for improving compressor efficiency.
[embodiment 10]
Figure 10 is the structure chart of the partial longitudinal section of the heat pump assembly for illustrating schematically that embodiments of the present invention 10.Separately
Outward, with 9 identical part of embodiment, mark same reference, clipped explanation.In addition, each portion
Position is the position for schematically depicting, and the present invention is not limited to the form for illustrating.
(Teat pump hot water supply device)
In Fig. 10, heat pump assembly (hereinafter referred to as " Teat pump hot water supply device ") 540, by the system shown in embodiment 9
Refrigerant compressor 510, radiator 102, expansion valve 103, vaporizer 104 and link them successively and make the cold-producing medium of refrigerant cycle
Pipe arrangement 105 is implementing freeze cycle.
That is, as Teat pump hot water supply device 540 has the coolant compressor 510 shown in embodiment 9, thus it is possible to
Reduce dissolubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium, acquisition improves the effect of heat pump efficiency.
In addition, also can be according to the Teat pump hot water supply device 140 shown in embodiment 2, will be using fluid circuit 130 and radiating
Device 102 carries out thermally coupled (with reference to Fig. 2).
[other embodiments]
More than, in embodiment 1～8, as to the 1st (downside) discharge duct 35 and the 2nd (upside) discharge duct 45
In the mechanism that is adjusted of flow path resistance, show the mechanism that the 1st valve 37 and the 2nd valve 47 are set, but the invention is not restricted to this,
Also can be using other mechanisms such as flow path cross sectional area, the adjustment of length, stream bending, capillary tube.
In addition, as the adiabatic mechanism for preventing lubricating oil from radiating from the wall facing external of hermetic container 8, although show
Between the wall of heat exchange mechanism and hermetic container 8, the component 55 of the flowing of the above-mentioned lubricating oil of configuration blocking is come the adiabatic engines that constitute
Structure, but be also effective by the outside wall surface of hermetic container 8 mechanism adiabatic with exogenous QI.
Also, the cylinder structure figure of the Rotary Compressor of imagination utilized above is illustrated, even in reciprocating, whirlpool
In the case of the compressor mode such as rotating, as long as can configure the compressor of 2 discharge duct, then same effect can be obtained.
Symbol description：
1：Compressor suction tube, 3：Compression mechanism, 5：Intermediate plate, 6：Drive shaft, 7a：Short axle side bearing, 7b：Major axis side axle
Hold, 8：Hermetic container, 9：Motor, 10：1st (downside) compression mechanism, 11：1st (downside) cylinder, 11a：1st (downside) cylinder pressure
Contracting room, 15：1st (downside) cylinder suction tube, 17：1st (downside) outlet, 20：2nd (upside) compression mechanism, 21：2nd (on
Side) cylinder, 21a：2nd (upside) cylinder discharge chambe, 25：2nd (upside) cylinder suction tube, 27：2nd (upside) outlet, 30：1st row
Outbound path, 31：1st (downside) discharge acoustic filter, 32：1st (downside) discharge muffler space, 33：Container, 35：1st (downside)
Discharge duct, 36：Heat exchange mechanism, 37：Valve, 38：Fin, 39：1st discharge path, 40：2nd discharge path, 41：2nd (on
Side) discharge acoustic filter, 42：2nd (upside) discharge muffler space, 43：Container, 45：2nd (upside) discharge duct, 46：Connection
Stream, 47：Valve, 50：Oil stock portion, 51：Oil rotary pump, 52：Fuel feed pump, 55：Oil surround mechanism, 56：Oily return loop, 57：
Oil eliminator, 60：Compression mechanism, 61：Compression cylinder, 61a：Cylinder discharge chambe, 65：Cylinder suction tube, 90：Hermetic container base, 70：The
1 discharge path, 71：1st discharge acoustic filter, 72：1st discharge muffler space, 73：Container, 75：1st discharge duct, 76：Heat
Exchange mechanism, 77：Valve, 78：Fin, 79：1st outlet, 80：2nd discharge path, 81：2nd discharge acoustic filter, 82：2nd row
Go out muffler space, 83：Container, 85：2nd discharge duct, 87：Valve, 89：2nd outlet, 102：Radiator, 103：Expansion valve,
104：Vaporizer, 105：Refrigerant piping, 110：2 cylinder compressor of low-pressure shell type (coolant compressor, embodiment 1),
120：Coolant compressor, 130：Using fluid circuit, 140：Teat pump hot water supply device (embodiment 2), 210：Low-pressure shell
2 cylinder compressor of type (coolant compressor, embodiment 3), 220：Main refrigerant circuit, 240：Heat pump assembly (embodiment 4),
310：2 cylinder compressor of low-pressure shell type (coolant compressor, embodiment 5), 320：Main refrigerant circuit, 340：Heat pump assembly
(embodiment 6), 410：2 cylinder compressor of low-pressure shell type (coolant compressor, embodiment 7), 420：Main refrigerant circuit,
440：Heat pump assembly (embodiment 8), 510：1 cylinder compressor of low-pressure shell type (coolant compressor, embodiment 9), 540：
Teat pump hot water supply device (embodiment 10).
Claims (12)
1. a kind of coolant compressor, it is characterised in that：Hermetic container with low-pressure shell type, compression mechanism, motor, oil
Storage portion, heat exchange mechanism and multiple discharge paths；
The compression mechanism is accommodated in the hermetic container, is sucked and compression refrigerant；
The motor is accommodated in the hermetic container, and the compression mechanism is driven；
The oil stock portion is formed in the bottom in the hermetic container, and lubricating oil is stored；
The heat exchange mechanism be stored in the lubricating oil in the oil stock portion and the cold-producing medium discharged from the compression mechanism it
Between carry out heat exchange；
The plurality of discharge path by cold-producing medium from the compression mechanism to the hermetic container outside guide；
The discharge path possesses the 1st discharge path and the 2nd discharge path, and the 1st discharge path has in the hermetic container
The standby heat exchange mechanism heated by the lubricating oil, the 2nd discharge path by the cold-producing medium not with the lubrication
Oil with carrying out heat exchange to outside the hermetic container guide, the 1st discharge path after the heat exchange mechanism with
2nd discharge path converges.
2. coolant compressor according to claim 1, it is characterised in that：With in the system discharged from the compression mechanism
Cryogen by the bypass flow path of the 1st discharge path and the 2nd discharge path is connected before the heat exchange mechanism, also,
Possesses the stream resistance of the refrigerant flow that adjustment is flowed in the 1st discharge path and the 2nd discharge path respectively
Force mechanisms.
3. coolant compressor according to claim 1 and 2, it is characterised in that：By described in flow path resistance mechanism controls
The temperature in oil stock portion, the flow path resistance institutional adjustment flow in the 1st discharge path and the 2nd discharge path respectively
Refrigerant flow.
4. coolant compressor according to claim 1 and 2, it is characterised in that：The compression mechanism is by the 1st compression mechanism
The two compression mechanisms are constituted with the 2nd compression mechanism, and the 1st compression mechanism is by the cold-producing medium of boil down to high pressure from the described 1st
Discharge path is guided to the outside of the hermetic container, and the 2nd compression mechanism is by the cold-producing medium of boil down to high pressure from the described 2nd
Discharge path is guided to the outside of the hermetic container.
5. coolant compressor according to claim 2, it is characterised in that：The compression mechanism by the 1st compression mechanism and
2nd compression mechanism the two compression mechanisms are constituted, and the 1st compression mechanism is by the cold-producing medium of boil down to high pressure from the 1st row
The outside guiding of the outlet radial direction hermetic container, the 2nd compression mechanism is by the cold-producing medium of boil down to high pressure from the 2nd row
The outside guiding of the outlet radial direction hermetic container,
It is provided with that the high-pressure refrigerant from after the 1st compression mechanism discharge is flowed into and connects with the 1st discharge path
The 1st discharge acoustic filter；
It is provided with that the high-pressure refrigerant from after the 2nd compression mechanism discharge is flowed into and connects with the 2nd discharge path
The 2nd discharge acoustic filter；Also,
With the bypass flow path for making the 1st discharge acoustic filter connect with the described 2nd discharge acoustic filter.
6. coolant compressor according to claim 4, it is characterised in that：1st compression mechanism and the 2nd compression
Mechanism is the dual rotation type compressor that action is compressed in antiphase.
7. coolant compressor according to claim 4, it is characterised in that：The hermetic container possesses prevents the lubrication
The adiabatic mechanism that oil radiates from the wall facing external of the hermetic container.
8. coolant compressor according to claim 1, it is characterised in that：In the 1st discharge path by described
A part for the scope in oil stock portion is provided with heat exchange mechanism, matches somebody with somebody between the wall of the heat exchange mechanism and the hermetic container
Put and the oil of the flowing blocking of the lubricating oil is surrounded into mechanism.
9. coolant compressor according to claim 1, it is characterised in that：The lubricating oil is mixed with hydrocarbon refrigerant
Property is little.
10. coolant compressor according to claim 9, it is characterised in that：The lubricating oil is using containing oxirane
Alkyl diol so that under 40 DEG C, atmospheric pressure kinematic viscosity be more than 18cSt.
11. coolant compressors according to claim 1, it is characterised in that：The compression mechanism by the 1st compression mechanism and
The 2nd compression mechanism for being configured at the top of the 1st compression mechanism is constituted；
The coolant compressor has：
The 1st discharge acoustic filter that high-pressure refrigerant from after the 1st compression mechanism discharge is flowed into,
Connect with the 1st discharge acoustic filter, the 1st discharge path for directly being guided to the outside of the hermetic container,
The 2nd discharge acoustic filter that high-pressure refrigerant from after the 2nd compression mechanism discharge is flowed into, and
Connect with the 2nd discharge acoustic filter, the 2nd discharge path for directly being guided to the outside of the hermetic container, also,
Between the lubricating oil for being stored in the oil stock portion and the high-pressure refrigerant being flowed in the 1st discharge acoustic filter
Carry out heat exchange.
A kind of 12. heat pump assemblies, usage right require the coolant compressor any one of 1 to 11.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2012/003021 WO2013168193A1 (en) | 2012-05-09 | 2012-05-09 | Refrigerant compressor and heat pump device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104380009A CN104380009A (en) | 2015-02-25 |
| CN104380009B true CN104380009B (en) | 2017-05-03 |
Family
ID=49550280
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280073851.8A Expired - Fee Related CN104380009B (en) | 2012-05-09 | 2012-05-09 | Refrigerant compressor and heat pump device |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JP5889405B2 (en) |
| CN (1) | CN104380009B (en) |
| WO (1) | WO2013168193A1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3236075B1 (en) * | 2014-12-19 | 2024-03-20 | Fujitsu General Limited | Rotary compressor |
| EP3318822B1 (en) * | 2015-07-03 | 2020-11-25 | Mitsubishi Electric Corporation | Heat pump device |
| JP7044463B2 (en) | 2016-11-14 | 2022-03-30 | 株式会社富士通ゼネラル | Rotary compressor |
| CN108180680B (en) * | 2018-01-22 | 2023-08-22 | 珠海格力电器股份有限公司 | Oil return control device, air conditioning system and oil return control method thereof |
| CN108895570A (en) * | 2018-07-25 | 2018-11-27 | 珠海格力电器股份有限公司 | A kind of water pump attemperator and heat pump outdoor unit |
| CN109374831A (en) * | 2018-10-30 | 2019-02-22 | 天津商业大学 | Refrigerant and lubricating oil intermiscibility experimental apparatus for testing |
| KR102381160B1 (en) | 2020-03-06 | 2022-03-31 | 엘지전자 주식회사 | A compressor |
| BE1029292B1 (en) * | 2021-04-09 | 2022-11-16 | Atlas Copco Airpower Nv | Element, device and method for compressing gas to be compressed at a low temperature |
| CN115435230B (en) * | 2022-09-02 | 2024-01-16 | 江森自控空调冷冻设备(无锡)有限公司 | Method for controlling viscosity of lubricating oil of centrifugal compressor |
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|---|---|---|---|---|
| JP2006105458A (en) * | 2004-10-04 | 2006-04-20 | Mitsubishi Electric Corp | Refrigerant circulation system and hermetic compressor |
| CN101275568A (en) * | 2007-03-30 | 2008-10-01 | 富士通将军股份有限公司 | Injectible two-staged rotary compressor and heat pump system |
| JP2009097486A (en) * | 2007-10-19 | 2009-05-07 | Mitsubishi Heavy Ind Ltd | Compressor |
| JP2009250111A (en) * | 2008-04-07 | 2009-10-29 | Daikin Ind Ltd | Compressor |
| JP2009264322A (en) * | 2008-04-28 | 2009-11-12 | Mitsubishi Electric Corp | Scroll compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6115270Y2 (en) * | 1978-11-30 | 1986-05-12 | ||
| JP4436716B2 (en) * | 2004-06-14 | 2010-03-24 | パナソニック株式会社 | vending machine |
| JP2010261679A (en) * | 2009-05-11 | 2010-11-18 | Panasonic Corp | Refrigerating cycle |
-
2012
- 2012-05-09 WO PCT/JP2012/003021 patent/WO2013168193A1/en active Application Filing
- 2012-05-09 CN CN201280073851.8A patent/CN104380009B/en not_active Expired - Fee Related
- 2012-05-09 JP JP2014514228A patent/JP5889405B2/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006105458A (en) * | 2004-10-04 | 2006-04-20 | Mitsubishi Electric Corp | Refrigerant circulation system and hermetic compressor |
| CN101275568A (en) * | 2007-03-30 | 2008-10-01 | 富士通将军股份有限公司 | Injectible two-staged rotary compressor and heat pump system |
| JP2009097486A (en) * | 2007-10-19 | 2009-05-07 | Mitsubishi Heavy Ind Ltd | Compressor |
| JP2009250111A (en) * | 2008-04-07 | 2009-10-29 | Daikin Ind Ltd | Compressor |
| JP2009264322A (en) * | 2008-04-28 | 2009-11-12 | Mitsubishi Electric Corp | Scroll compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP5889405B2 (en) | 2016-03-22 |
| CN104380009A (en) | 2015-02-25 |
| WO2013168193A1 (en) | 2013-11-14 |
| JPWO2013168193A1 (en) | 2015-12-24 |
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