CN104380009A - Refrigerant compressor and heat pump device - Google Patents

Refrigerant compressor and heat pump device Download PDF

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Publication number
CN104380009A
CN104380009A CN201280073851.8A CN201280073851A CN104380009A CN 104380009 A CN104380009 A CN 104380009A CN 201280073851 A CN201280073851 A CN 201280073851A CN 104380009 A CN104380009 A CN 104380009A
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CN
China
Prior art keywords
discharge
discharge path
oil
compressing mechanism
closed container
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.)
Granted
Application number
CN201280073851.8A
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Chinese (zh)
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CN104380009B (en
Inventor
横山哲英
关屋慎
佐佐木圭
河村雷人
幸田利秀
前山英明
加藤太郎
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Publication of CN104380009A publication Critical patent/CN104380009A/en
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Publication of CN104380009B publication Critical patent/CN104380009B/en
Expired - Fee Related legal-status Critical Current
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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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • 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
    • 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
    • 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
    • F25B2500/12—Sound
    • 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

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

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

Coolant compressor and heat pump assembly
Technical field
The present invention relates to coolant compressor and heat pump assembly, particularly relate to the coolant compressor used in the heat pump assemblies such as fridge-freezer, air conditioner or hot-water supply device and the heat pump assembly using this compressor.
Background technology
In recent years, in coolant compressor, from the view point of seeking to prevent global warming, need the technology that the freon refrigeration dosage used is cut down, the technology using the combustible refrigerant that depletion of the ozone layer coefficient is zero, global warming coefficient is little.
The hydrocarbon refrigerant (hereinafter referred to as " HC cold-producing medium ") that particularly refrigerant property is superior is expected.HC cold-producing medium, from the view point of sliding part greasy property, spill sealing property, theoretical COP, possess the refrigerant property equal with freon refrigerant, the fridge-freezer employing iso-butane is produced in batches, but from the danger of combustible refrigerant, cold-producing medium allows that charging quantity limits by international standard.Such as, according to IEC standard, within needing the hydrocarbon refrigerant amount that can be filled in home-use air conditioner to be cut to about 150g.
Therefore, the means of filling quantitative limitation are allowed as solution cold-producing medium, report following content, namely, PAG (PAG) is low with the intermiscibility of HC cold-producing medium (R290), by PAG is used as lubricating oil, refrigerant charge amount (no longer needing predict meltage in lubricating oil and enclose refrigerant amount extraly) (for example, referring to non-patent literature 1) can be reduced.
In addition, disclose an invention, in the invention, by using the oil (non-compatibility oiling) low with the intermiscibility of HC cold-producing medium as lubricating oil, and, make to become cold-producing medium suction pressure environment (low-pressure shell) in the closed shell of storage lubricating oil (closed container), reduce the meltage (for example, referring to patent document 1) of HC cold-producing medium relative to lubricating oil.
In addition, also there is a problem, if that is, use the lubricating oil relative to HC cold-producing medium with non-compatibility property, then the lubricating oil be carried in freeze cycle can not turn back in compressor fully.In order to head it off, disclose an invention, this invention adopts High Pressure Shell type compressor or middle die mould compressor, use has HC cold-producing medium and holds the paraffin series mineral oil of diffluent character as lubricating oil, be arranged in the running of compressor the heating arrangements that the lubricating oil in compressor heats, the refrigerant amount be dissolved in lubricating oil is made to reduce (for example, referring to patent document 2).
Prior art document
Patent document
Patent document 1: Japanese Unexamined Patent Publication No. 8300224 publications (2-3 page, Fig. 1)
Patent document 2: Japanese Unexamined Patent Publication 11-294877 publication (3-4 page, Fig. 3)
Non-patent literature
Non-patent literature 1: high bridge benevolence " characteristic of cold-producing medium/refrigerator oil mixture ", Japan Refrigeration and Air Conditioning Industry Association sponsors, alternative refrigerant and environment international symposium 2002 collection of thesis 160-164 page
Summary of the invention
Invent problem to be solved
But, in patent document 1, cutting down in the meltage of cold-producing medium in lubricating oil although disclose, non-compatibility oiling and low-pressure shell are effective means, but do not consider that inventor waits the size of the dynamic viscosity change of the lubricating oil that is such, that caused by the change of the operating condition in the compressor of low-pressure shell form found in following test evaluation etc.
In addition, patent document 2 is also only the compressor describing High Pressure Shell or middle swaging formula, does not consider low-pressure shell.
So about the compressor of low-pressure shell form, by carrying out the following test evaluation etc. of Performance comparision with the compressor of High Pressure Shell form, problem such below becomes clear and definite.
(experimental condition)
Inventors etc., in order to propose the new problem brought by low-pressure shell and non-compatibility oiling, use R290 as HC cold-producing medium, implement the low-pressure shell type Rotary Compressor of 1.5 horse power grades and the performance test of High Pressure Shell type Rotary Compressor.
Figure 11 is the figure of the condition (hereinafter referred to as " compressor experimental condition ") arranging such performance test, specifiedly heats refrigeration test condition in the middle of experimental condition, (e), 8 conditions that (f) European hot water supply heats A2W35 condition and (g) Chinese GB condition implement respectively about refrigeration test condition in the middle of (a) ASHRAE-T condition, (b) specified refrigeration test condition, (c), (d).
Now, viscosimeter (the online viscosimeter 1600 of Cambridge company) is installed at the bottom of compressor housing, use R290 as HC cold-producing medium, the naphthene series mineral oil (NM100) high about the intermiscibility as lubricating oil and 2 levels containing the low PAG oil of the intermiscibility of EO50%, determine oily dynamic viscosity during each running.
(R290 and naphthene series mineral oil)
Figure 12 uses R290 as HC cold-producing medium, uses the high naphthene series mineral oil (NM100) of intermiscibility as lubricating oil, implements measurement result when above-mentioned each test, represents the dynamic viscosity change of this lubricating oil.
As shown in Figure 12, when low-pressure shell type compressor, compared with High Pressure Shell type compressor, oily dynamic viscosity is high, such as specifiedly reaches about 5 times when heating running, and mechanical loss becomes very large.And, oil dynamic viscosity amplitude of fluctuation is also large, the ratio of maximum (during middle refrigeration test condition) and minimum of a value while heating experimental condition (specified) reaches about 7 times, so, be difficult to take into account bearing durability over a wide range of conditions and guarantee and the design that mechanical loss reduces.
In low-pressure shell type compressor, use HC cold-producing medium like this, use the high naphthene series mineral wet goods mineral oil of intermiscibility as under lubrication oil condition, learn to there is following problem, namely, oil dynamic viscosity amplitude of fluctuation is large, is difficult to take into account bearing durability over a wide range of conditions and guarantees that (wishing that viscosity is large) and mechanical loss reduce the design of (wishing that viscosity is little).
(R290 and PAG oil)
Oil change is become the result implementing same test here containing the PAG oil (, use viscosity is this PAG oil of VG22) that the intermiscibility of EO50% is low by Figure 13, represents the dynamic viscosity change of this lubricating oil.
As shown in Figure 13, when low-pressure shell type compressor, compared with High Pressure Shell type compressor, oil dynamic viscosity specified heat running time be about 2.5 times, in addition, it is about 2 times as the maximum (when centre heats experimental condition) of oily dynamic viscosity amplitude of fluctuation and the ratio of minimum of a value (middle refrigeration test condition).
The PAG oil use HC cold-producing medium like this in low-pressure shell type compressor, using intermiscibility low is as under lubrication oil condition, and oily dynamic viscosity amplitude of fluctuation and use naphthene series mineral wet goods mineral oil diminish as lubricating compared with oil condition.
In addition, about the solubility of HC cold-producing medium and PAG oil, the solubility curve of R290 (propane) cold-producing medium and main lubricating oil (mineral oil, POE oil, PAG are oily) has been shown in non-patent literature 1, can learn from these solubility curves, alkyl diol (PAG) oil phase is low for the intermiscibility of HC cold-producing medium, with the oil phase ratio of mineral wet goods intermiscibility, the change of refrigerant dissolves degree is little, can cut down HC cold-producing medium enclosed volume.
By using the PAG oil low relative to the intermiscibility of HC cold-producing medium as lubricating oil like this in low-pressure shell, with use mineral oil as lubricating compared with oil condition, oily dynamic viscosity amplitude of fluctuation can be reduced, in addition, the meltage of HC cold-producing medium in lubricating oil (refrigerant charge amount can be reduced) can be reduced by non-compatibility oiling and low-pressure shellization.
But, from the view point of guaranteeing to take into account the free degree that bearing durability guarantees the design reduced with mechanical loss, need the oily dynamic viscosity amplitude of fluctuation reducing PAG further.
In addition, if increase EO (oxirane) amount in PAG oil, then can reduce the intermiscibility (refrigerant charge amount can be reduced) relative to HC cold-producing medium, but produce lubricated sliding wear performance thus to reduce, time particularly more than 50%, produce the problem that lubricated sliding wear performance sharply reduces.Therefore, as the countermeasure of the reduction of the lubricated sliding wear performance caused increase EO amount, certain means that the oily dynamic viscosity of PAG is controlled are needed.
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 uprises, and burning-point reduces.Under VG18 (ISO viscosity criterion), burning-point is 183 DEG C, and VG18 is the limit of the viscosity that can use in actual applications.From the limit that the viscosity of the standard state of such PAG oil reduces, also need certain means that the oily dynamic viscosity of PAG is controlled.
(excursion of refrigerant dissolves degree)
Figure 14 be when low-pressure shell type and High Pressure Shell type when compare the figure of the excursion of the refrigerant dissolves degree relative to temperature and pressure.
Figure 15 be when low-pressure shell type and High Pressure Shell type when oily dynamic viscosity when comparing refrigerant dissolves the figure of excursion.
Usually, as shown in Figure 14, when the curve map represented the relation of refrigerant dissolves degree and pressure represents pressure 0 about variant temperature conditions, refrigerant dissolves degree becomes the logarithmic curve of 0.Namely, in the closed shell (closed container) making storage lubricating oil for cold-producing medium discharge the High Pressure Shell type in pressure ring border, if the discharge press strip part change of compressor, be then stored at the pressure, temperature variation of the oil in closed shell (closed container).On the other hand, when low-pressure shell type, if the suction pressure condition change of compressor, be then stored at the pressure, temperature variation of the oil in closed shell (closed container).
From the characteristic of such line of can writing music with the refrigerant dissolves that logarithmic curve represents of Figure 14, in low-temp low-pressure side, the low-pressure shell type of pressure, temperature variation is compared with High Pressure Shell type, and the impact applied refrigerant dissolves degree is larger, and the change of refrigerant dissolves degree is also larger.Its result, as shown in Figure 5, oily dynamic viscosity excursion is also than larger in High Pressure Shell type in low-pressure shell type.
As described above, in order to tackle low-pressure shell and non-compatibility oiling, following such new problem is proposed.
(1) as the means of the refrigerant dissolves degree of reduction HC cold-producing medium, although the PAG oil using non-compatibility property is effective, in fact PAG oil can not manufacture the low oil of ratio of viscosities VG18.Therefore, in order to make design bearing optimization, reduce mechanical loss, other the means that the physical property of PAG oil is controlled are needed.
(2) and, when use low-pressure shell form, the refrigerant dissolves degree and the dynamic viscosity that are stored at the oil in closed shell (closed container) easily change.Therefore, in order to make design bearing optimization, reduce mechanical loss, the new means that oils is controlled are needed.
The present invention makes to solve problem as described above, its object is to obtain a kind of coolant compressor and heat pump assembly, this coolant compressor and heat pump assembly can reduce solubility in the oil of cold-producing medium in the compressor of low-pressure shell form, cut down cold-producing medium enclosed volume, further, compressor efficiency can be improved.
For solving the means of problem
The feature of coolant compressor of the present invention is: have the closed container of low-pressure shell type, compressing mechanism, motor and oil stock portion;
This compressing mechanism is accommodated in this closed container, sucks and compressed refrigerant;
This motor is accommodated in above-mentioned closed container, drives compression mechanism;
This oil stock portion is formed in the bottom in above-mentioned closed container, stores lubricating oil;
Described coolant compressor has and is being stored in the mechanism carrying out heat exchange between the lubricating oil in above-mentioned oil stock portion and the high-pressure refrigerant of discharging from compression mechanism.
The effect of invention
In the present invention, because the heat energy had from the high-pressure refrigerant of compressing mechanism discharge is handed over to be stored at the lubricating oil oil stock portion, so, solubility in the oil of cold-producing medium can be reduced, therefore, it is possible to obtain the effect of cutting down cold-producing medium enclosed volume and the effect improving compressor efficiency and heat pump efficiency.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the coolant compressor that embodiments of the present invention 1 are schematically described.
Fig. 2 is the structure chart of the heat pump assembly that embodiments of the present invention 2 are schematically described.
Fig. 3 is the longitudinal section of the coolant compressor that embodiments of the present invention 3 are schematically described.
Fig. 4 is the structure chart of the heat pump assembly that embodiments of the present invention 4 are schematically described.
Fig. 5 is the longitudinal section of the coolant compressor that embodiments of the present invention 5 are schematically described.
Fig. 6 is the structure chart of the heat pump assembly that embodiments of the present invention 6 are schematically described.
Fig. 7 is the longitudinal section of the coolant compressor that embodiments of the present invention 7 are schematically described.
Fig. 8 is the structure chart of the heat pump assembly that embodiments of the present invention 8 are schematically described.
Fig. 9 is the longitudinal section of the coolant compressor that embodiments of the present invention 9 are schematically described.
Figure 10 is the structure chart of the heat pump assembly that embodiments of the present invention 10 are schematically described.
Figure 11 is the condition of low-pressure shell type and High Pressure Shell type and performance test.
Figure 12 is the longitudinal section of the sealed electrical compressor that embodiments of the present invention 6 are described.
Figure 13 is as the measurement result under lubrication oil condition using R290 and naphthene series mineral oil.
Figure 14 is the measurement result of the change of the refrigerant dissolves degree represented relative to temperature and pressure.
Figure 15 is the measurement result of the relation representing refrigerant dissolves degree and oily dynamic viscosity.
Detailed description of the invention
[embodiment 1]
Fig. 1 is the longitudinal section of the coolant compressor that embodiments of the present invention 1 are schematically described.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(low-pressure shell type 2 cylinder compressor)
In FIG, coolant compressor (hereinafter referred to as " low-pressure shell type 2 cylinder compressor " or " coolant compressor ") 110 has closed container 8, be arranged on the motor 9 in closed container 8, the driving shaft 6 driven by motor 9, the minor axis side bearing the 7a respectively two ends of driving shaft 6 supported and major axis side bearing 7b, the 1st (downside) compressing mechanism 10 be made up of the 1st (downside) cylinder 11, the 2nd (upside) compressing mechanism 20 be made up of the 2nd (upside) cylinder 21, with the intermediate plate 5 separated the 1st (downside) cylinder the 11 and the 2nd (upside) cylinder 21.
The cold-producing medium of low pressure is inhaled in closed container 8 from compressor suction line 1, mobile in closed container 8, be attracted in the 1st (downside) cylinder discharge chambe 11a of the 1st (downside) compressing mechanism 10 from being arranged on the 1st in closed container 8 (downside) cylinder suction line 15, further, be attracted in the 2nd (upside) cylinder discharge chambe 21a of the 2nd (upside) compressing mechanism 20 by from the 2nd (upside) cylinder suction line 25.
Then, respectively in the 1st (downside) cylinder discharge chambe 11a and the 2nd (upside) cylinder discharge chambe 21a by the cold-producing medium (hereinafter referred to as " high-pressure refrigerant ") that have compressed, be discharged to the 1st (downside) from the 1st (downside) outlet the 17 and the 2nd (upside) outlet 27 respectively and discharge muffler space 32 and the 2nd (upside) is discharged muffler space 42, be connected with the 2nd (upside) discharge duct 45 with the 1st (downside) discharge duct 35 guided to the refrigerant loop (not shown) outside closed container 8 respectively.In addition, the 1st (downside) is discharged muffler space 32 and is formed by container 33, both merging is called silencer 31 is discharged in the 1st (downside).
In the 1st (downside) discharge duct the 35 and the 2nd (upside) discharge duct 45, be respectively arranged with the 1st valve 37 and the 2nd valve 47 that carry out the pressure adjustmenting mechanism adjusted as flow path resistance, by regulating respective aperture, suitably adjust the refrigerant flow of flowing in the 1st (downside) discharge duct the 35 and the 2nd (upside) discharge duct 45 respectively.
In addition, the 1st (downside) discharge duct 35 discharge from the 1st (downside) muffler space 32 via the heat exchange mechanism 36 in the oil stock portion 50 be arranged in closed container 8 after, guided by the outside to closed container 8.
In the structure of embodiments of the present invention 1, the discharge path 30,40 that the high-pressure refrigerant that 2 compression cylinders 11,21 are discharged from outlet 17,27 respectively guides to radiator 102 (with reference to Fig. 2) is formed as described above.Wherein, the discharge path heated lubricating oil in closed container is defined as the 1st.
In vertical compressor, because lubricating oil is stored in the bottom in closed container 8, so general structure is the discharge path called after the 1st by being configured at downside, will be configured at the discharge path called after the 2nd of upside.But, also sometimes adopt following structure, that is, discharge path called after the 1st, the 1st discharge path carrying out heat exchange in closed shell energetically is relatively configured at compared with the 2nd discharge path upside.
Heat exchange mechanism 36 is configured near the suction inlet of oil rotary pump 51 of the lower end being installed on driving shaft 6, and the oil being configured for the flowing blocking lubricating oil between heat exchange mechanism 36 and the outside wall portions of closed container 8 surrounds mechanism 55, seeks thermal insulation.The heat-transfer pipe of more than 1 or 2 that heat exchange mechanism 36 is such as flowed by cold-producing medium and the multiple heat sinks (fin) be arranged on this heat-transfer pipe are formed, and are submerged in lubricating oil.
1st (downside) is discharged muffler space 32 and is discharged muffler space 42 with the 2nd (upside) and be communicated with by being communicated with stream 46.In addition, stream 46 through in the axial direction the 1st (downside) cylinder the 11, the 2nd (upside) cylinder 21 and intermediate plate 5 is communicated with.In addition, the 2nd (upside) is discharged muffler space 42 and is formed by container 43, both merging is called silencer 41 is discharged on top.
Such as, at low ambient conditions, there are the following problems, that is, because inlet temperature reduces, the oil temperature be stored in closed container reduces, and oil viscosity increases, and the mechanical loss of compressor increases.
In embodiments of the present invention 1, by making the 2nd valve 47 throttling, 1st valve 37 is opened, compressed by the 1st compression cylinder 11, be discharged to the 1st from the 1st outlet 17 and discharge high-pressure refrigerant muffler space 32, flow to the 2nd discharge muffler space 42 by being communicated with stream 46, so, the flow flowing through the 2nd (upside) discharge duct 45 can be made to reduce, the flow flowing through the 1st (downside) discharge duct 35 is increased.That is, because increased by the flow of the oil of heat exchange mechanism 36, therefore, by increasing with the heat exchange amount (quantities received of heat energy) of oil, oil temperature rises, and obtains the effect that oil viscosity reduces.
According to above explanation, low-pressure shell type 2 cylinder compressor 110 of embodiment 1 can control oil temperature, therefore, in the oil of cold-producing medium, solubility and oily dynamic viscosity amplitude of fluctuation diminish, and obtain the effect of cutting down cold-producing medium enclosed volume and the effect that compressor efficiency is improved.
In addition, because the oil being placed with the flowing for blocking lubricating oil between heat exchange mechanism 36 and the wall of closed container 8 surrounds mechanism 55, so surround the inside of mechanism 55 at oil, heating lubricating oil, prevents heat energy to the dissipation of the outside of closed container 8.
In addition, as lubricating oil, use the lubricating oil little with the intermiscibility of hydrocarbon refrigerant, such as, use the alkyl diol containing oxirane, with make 40 DEG C, dynamic viscosity under atmospheric pressure is at more than 18cSt.
[embodiment 2]
Fig. 2 is the structure chart of the partial longitudinal section of the heat pump assembly that embodiments of the present invention 2 are schematically described.In addition, in the part identical with embodiment 1, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(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 utilizes fluid circuit 130.Main refrigerant circuit 120, by coolant compressor 110, radiator 102, expansion valve 103, evaporimeter 104, links them successively and makes the refrigerant piping 105 of refrigerant circulation realize freeze cycle.
Here, coolant compressor 110 is that low-pressure shell type 2 cylinder compressor the 110,1st (downside) discharge duct the 35 and the 2nd (upside) discharge duct 45 illustrated in embodiment 1 is converged in the downstream (outside of closed container 8) of the 1st valve 37 and the 2nd valve 47 respectively.
And, in radiator 102, the fluid (being water) that utilizes of fluid circuit 130 is utilized to carry out heat exchange by the cold-producing medium (high-pressure refrigerant) that makes coolant compressor 110 have compressed here with flowing through, cold-producing medium is transferred heat energy and is cooled, and utilizes fluid receive heat energy and heated.That is, utilize fluid circuit 130 effectively to utilize and utilized fluid by warmed-up in radiator 102.
Now, in Teat pump hot water supply device 140, need to discharge formed high-boiling by high temperature and operate.In the case, by closing the 1st valve 37, opening the 2nd valve 47, the flow of flowing in the 2nd (upside) discharge duct 45 can be made to increase.That is, the high temperature refrigerant not carrying out heat exchange with oil can be supplied to radiator 102.
On the other hand, when needing high output with normal leaving water temperature, because coolant compressor 110 carries out action with high rotating speed, the large pressure loss is there is in discharge portion, so, in order to reduce the pressure loss, make the 1st valve 37 and the ground action of the 2nd valve 47 standard-sized sheet.
And, in order to reduce to be produced by pressure fluctuation noise, vibration, discharge with the 2nd (upside) pressure fluctuation occurred with antiphase between muffler space 42 reciprocally propagate via being communicated with stream 46 by making to discharge in the 1st (downside) muffler space 32, the effect of the amplitude reducing pressure fluctuation can be obtained.
In addition, the control of the aperture of the 1st valve 37 and the 2nd valve 47, the oil temperature in one side detection closed container 8, the outside wall temperature of closed container 8 or discharge temperature, one side controls actively, or according to purposes, environmental condition, is adjusted to aperture most effective fifty-fifty.
According to above explanation, the Teat pump hot water supply device 140 of embodiment 2 has low-pressure shell type 2 cylinder compressor 110 of embodiment 1, so, solubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium can be reduced, the effect of the heat pump efficiency that is improved.
[embodiment 3]
Fig. 3 is the longitudinal section of the coolant compressor that embodiments of the present invention 3 are schematically described.In addition, in the part identical with embodiment 1, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(low-pressure shell type 2 cylinder compressor)
In figure 3, coolant compressor (hereinafter referred to as " low-pressure shell type 2 cylinder compressor ") 210 is provided with oily return loop 56.This oily return loop 56, after having been carried out oily separation at the cold-producing medium flowed out from a side of the 1st (downside) discharge duct the 35 and the 2nd (upside) discharge duct 45 or two sides in refrigerant loop (not shown), separated oil is turned back in the 1st (downside) compressing mechanism the 10 and the 2nd (upside) compressing mechanism 20.
Namely, in low-pressure shell type 2 cylinder compressor 210, in the same manner as low-pressure shell type 2 cylinder compressor 110 shown in embodiment 1, the 1st (downside) discharge duct 35 to discharge from the 1st (downside) muffler space 32 via the heat exchange mechanism 36 the oil stock portion 50 be arranged in closed container 8 after, be directed to the outside of closed container 8, in heat exchange mechanism 36, lubricating oil is heated, so, the effect of cutting down cold-producing medium enclosed volume and the effect improving compressor efficiency can be obtained.
And, by regulating the aperture of the 1st valve 37 and the 2nd valve 47, suitably adjust the refrigerant flow of flowing in the 1st discharge duct 35 and the 2nd discharge duct 45 respectively, so, in order to reduce the pressure loss in discharge duct, valve 37,47 standard-sized sheet can be made, on the other hand, when need to increase with the heat exchange amount of oil, make that oily dynamic viscosity reduces, refrigerant dissolves degree reduces, can carry out making the 1st valve 37 standard-sized sheet, close the adjustment such as the 2nd valve 47, to the reduction of cold-producing medium enclosed volume and the improvement of compressor efficiency effective.
Now, the function with the heat exchange amount of oil is adjusted by carrying out opening and closing adjustment to valve 37,47 in order to obtain, configurable connection stream 46, makes the cold-producing medium of discharging from compression cylinder can converge with the 2nd discharge path before the heat exchange mechanism 36 via the 1st discharge path side 35.
[embodiment 4]
Fig. 4 is the structure chart of the partial longitudinal section of the heat pump assembly that embodiments of the present invention 4 are schematically described.In addition, in the part identical with embodiment 3, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(Teat pump hot water supply device)
In the diagram, heat pump assembly 240 possesses by compressor 210, radiator 102, expansion valve 103, evaporimeter 104 and links them successively and make the refrigerant piping 105 of refrigerant circulation realize the main refrigerant circuit 220 of freeze cycle.Now, oil eliminator 57 is set between compressor 210 and radiator 102.
And, 1st (downside) discharge duct the 35 and the 2nd (upside) discharge duct 45 is converged in the downstream (outside of closed container 8) of the 1st valve 37 and the 2nd valve, temporarily be directed in oil eliminator 57, the cold-producing medium after oil is separated is guided by radiator 102.On the other hand, separated oil, is supplied (returning) to the 1st (downside) compressing mechanism the 10 and the 2nd (upside) compressing mechanism 20 by oily return loop 56.
According to above explanation, the heat pump assembly 240 of embodiment 4 has low-pressure shell type 2 cylinder compressor 110 of embodiment 1, so, solubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium can be reduced, the effect of the heat pump efficiency that is improved.In addition, also can, according to the Teat pump hot water supply device 140 shown in embodiment 2, be undertaken thermally coupled by utilizing fluid circuit 130 and radiator 102.
[embodiment 5]
Fig. 5 is the longitudinal section of the coolant compressor that embodiments of the present invention 5 are schematically described.In addition, in the part identical with embodiment 1, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(low-pressure shell type 2 cylinder compressor)
In Figure 5, coolant compressor (hereinafter referred to as " low-pressure shell type 2 cylinder compressor ") 310, be provided with by after via compressor suction line 1, the low pressure refrigerant be directed in closed container 8 is temporarily directed to the outside of closed container 8, the 1st (downside) the cylinder suction line 15 guided to the 1st (downside) cylinder discharge chambe 11a and the 2nd (upside) the cylinder suction line 25 guided to the 2nd (upside) cylinder discharge chambe 21a.Therefore, being cooled in main purposes with fridge-freezer, refrigerating plant etc., there is the effect reducing to suck loss on heating, superior compared with shown by embodiment 1.
In addition, the 1st (downside) pressure fluctuation from the firm discharge of the 1st (downside) compressing mechanism 10 being decayed in formation is discharged on the container 33 of silencer 31, multiple fins 38 of heat transmission are set, the fin of heat transmission self is not set at the 1st discharge path 35.Therefore, and use independently compared with heat exchanger (structure of the fin of heat transmission self is set at the 1st discharge path 35), favourable in cost degradation and densification.
That is, in low-pressure shell type 2 cylinder compressor 310, by discharging the heat transfer of muffler space 32 and fin 38 from the 1st (downside), lubricating oil is heated, so, the effect of cutting down cold-producing medium enclosed volume and the effect improving compressor efficiency can be obtained.
And, by regulating the aperture of the 1st valve 37 and the 2nd valve 47, suitably adjust the refrigerant flow of flowing in the 1st discharge duct 35 and the 2nd discharge duct 45 respectively, so, in order to reduce the pressure loss in discharge duct, valve 37,47 standard-sized sheet can be made, on the other hand, when need to increase with the heat exchange amount of oil, make that oily dynamic viscosity reduces, refrigerant dissolves degree reduces, can carry out making the 1st valve 37 standard-sized sheet, close the adjustment such as the 2nd valve 47, to the reduction of cold-producing medium enclosed volume and the improvement of compressor efficiency effective.
[embodiment 6]
Fig. 6 is the structure chart of the partial longitudinal section of the heat pump assembly that embodiments of the present invention 6 are schematically described.In addition, in the part identical with embodiment 5, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(Teat pump hot water supply device)
In figure 6, heat pump assembly 340 possesses by compressor 310, radiator 102, expansion valve 103, evaporimeter 104 and links them successively and make the refrigerant piping 105 of refrigerant circulation realize the main refrigerant circuit 320 of freeze cycle.
Therefore, heat pump assembly 340 has the coolant compressor 310 of embodiment 5, can reduce solubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium, so, the effect of the heat pump efficiency that can be improved.In addition, also can, according to the Teat pump hot water supply device 140 shown in embodiment 2, be undertaken thermally coupled by utilizing fluid circuit 130 and radiator 102.
[embodiment 7]
Fig. 7 is the longitudinal section of the coolant compressor that embodiments of the present invention 7 are schematically described.In addition, in the part identical with embodiment 5, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(low-pressure shell type 1 cylinder compressor)
Low-pressure shell type 2 cylinder compressor 310 shown in embodiment 5 is made up of these 2 compressing mechanisms of the 1st (downside) compressing mechanism the 10 and the 2nd (upside) compressing mechanism 20, but in the figure 7, coolant compressor 410 is low-pressure shell type 1 cylinder compressors that compressing mechanism is made up of 1 cylinder, and this is its difference.
Cylinder suction line 65 is provided with in this low-pressure shell type 1 cylinder compressor 410.Cylinder suction line 65, by after via compressor suction line 1, the low pressure refrigerant be directed in closed container 8 is temporarily directed to the outside of closed container 8, guides to cylinder discharge chambe 61a.Therefore, being cooled in main purposes with fridge-freezer, refrigerating plant etc., there is the effect reducing to suck loss on heating, superior compared with shown by embodiment 1.
In embodiments of the present invention 7, even without such connection stream 46 of embodiment 1 to 6, also because 2 outlets 27 of cylinder discharge chambe 61a, 17 are installed up and down dividually, so, even without connection stream, by making the 2nd valve 47 throttling, 1st valve 37 is opened, also become by the high-pressure refrigerant that have compressed in the 1st compression cylinder 61 and easily flow to the 2nd discharge muffler space 42 from cylinder discharge chambe 46, so, the flow of flowing in the 2nd (upside) discharge duct 45 can be made to reduce, the flow of flowing in the 1st (downside) discharge duct 35 is increased.That is, increased by the flow of the oil of heat exchange mechanism 36, so, by increasing with the heat exchange amount (quantities received of heat energy) of oil, the effect that oil temperature rises, oil viscosity reduces can be obtained.
In addition, although be provided with closed container base 90 on the bottom surface of the closed container 8 of coolant compressor 410, the form of closed container base 90 is not limited to illustrated form.In addition, in other embodiment 1 ~ 6, also can closed container base 90 be similarly set.
The structure same with embodiment 1 in addition, in low-pressure shell type 1 cylinder compressor 410, by regulating the aperture of the 1st valve 37 and the 2nd valve 47, suitably adjust the refrigerant flow of flowing in the 1st discharge duct 35 and the 2nd discharge duct 45 respectively, the effect of cutting down cold-producing medium enclosed volume and the effect improving compressor efficiency can be obtained.
[embodiment 8]
Fig. 8 is the structure chart of the partial longitudinal section of the heat pump assembly that embodiments of the present invention 8 are schematically described.In addition, in the part identical with embodiment 7, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(Teat pump hot water supply device)
In fig. 8, heat pump assembly 440 possesses by compressor 410, radiator 102, expansion valve 103, evaporimeter 104 and links them successively and make the refrigerant piping 105 of refrigerant circulation 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 solubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium, the effect of the heat pump efficiency that is improved.In addition, also can, according to the Teat pump hot water supply device 140 shown in embodiment 2, be undertaken thermally coupled by utilizing fluid circuit 130 and radiator 102.
[embodiment 9]
Fig. 9 is the longitudinal section of the coolant compressor that embodiments of the present invention 9 are schematically described.In addition, in the part identical with embodiment 7, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(low-pressure shell type 1 cylinder compressor: horizontal)
Above, in the such vertical compressor represented by embodiment 1 ~ 7, because lubricating oil is stored in the bottom in closed container 8, so, to the 1st discharge path that lubricating oil heats in closed container 8, to the discharge path called after the 1st of downside be configured at, the features simple structure of discharge path called after the 2nd of upside will be configured at, but will carry out the discharge path called after the 1st of heat exchange energetically in closed container 8, also can be the structure being relatively configured at upside compared with the 2nd discharge path sometimes.
In fig .9, the coolant compressor 510 shown in present embodiment 9, to become horizontal compressor suitable with the coolant compressor made shown in embodiment 7 (low-pressure shell type 1 cylinder compressor) 410.
In coolant compressor (low-pressure shell type 1 cylinder compressor) 510, discharge silencer 71 and the 1st in the major axis side bearing 7b side formation of supporting motor 9 side of driving mechanism 6 from the 1st outlet 77, the 1st of cylinder discharge chambe 61a discharge high-pressure refrigerant and discharge muffler space 72, the surface of the 1st discharge silencer container 73 arranges the fin 78 of the heat exchange of promotion and oil.The 1st discharge duct 75 guided from the 1st discharge muffler space 72 to radiator 102 and the valve 77 adjusted the aperture of the 1st discharge duct 75 are installed.
On the other hand, in minor axis side bearing 7a side, form the 2nd outlet 87, the 2nd and discharge silencer 81, the 2nd discharge muffler space 82, the 2nd discharge duct 85 guided from the 2nd discharge muffler space 72 to radiator 102 and the valve 87 adjusted the aperture of the 2nd discharge duct 85 are installed.By regulating the aperture of the 1st valve 77 and the 2nd valve 87, suitably adjust the refrigerant flow of flowing in the 1st discharge duct 75 and the 2nd discharge duct 85 respectively.
In addition, the end of a side of fuel feed pump 52 is connected with the minor axis side bearing 7a side of driving shaft 6, and the end of the opposing party of fuel feed pump 52 is positioned at oil stock portion 50.In addition, closed container base 90 is set in the side (cylindrical portion) of closed container 8.
Coolant compressor 510, in addition to the foregoing, the structure same with coolant compressor 410 (embodiment 7), because heated lubricating oil by the heat transfer of discharging muffler space 72 and fin 78 from the 1st, so, the effect of cutting down cold-producing medium enclosed volume and the effect improving compressor efficiency can be obtained.
[embodiment 10]
Figure 10 is the structure chart of the partial longitudinal section of the heat pump assembly that embodiments of the present invention 10 are schematically described.In addition, in the part identical with embodiment 9, mark the Reference numeral identical with it, clipped explanation.In addition, each position is the position schematically described, and the present invention is not defined to illustrated form.
(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 coolant compressor 510 shown in embodiment 9, radiator 102, expansion valve 103, evaporimeter 104 with link them successively and make the refrigerant piping 105 of refrigerant circulation implement freeze cycle.
That is, because Teat pump hot water supply device 540 has the coolant compressor 510 shown in embodiment 9, so, solubility and oily dynamic viscosity amplitude of fluctuation in the oil of cold-producing medium can be reduced, the effect of the heat pump efficiency that is improved.
In addition, also according to the Teat pump hot water supply device 140 shown in embodiment 2, can be undertaken utilizing fluid circuit 130 and radiator 102 thermally coupled (with reference to Fig. 2).
[other embodiment]
Above, in embodiment 1 ~ 8, as the mechanism adjusted the flow path resistance in the 1st (downside) discharge duct the 35 and the 2nd (upside) discharge duct 45, show the mechanism that the 1st valve 37 and the 2nd valve 47 are set, but the present invention is not limited thereto, also can use other the mechanism such as the adjustment of flow path cross sectional area, length, stream bending, capillary.
In addition, as the adiabatic mechanism that the wall preventing lubricating oil from closed container 8 externally dispels the heat, although show the adiabatic mechanism that the component 55 that configures the flowing blocking above-mentioned lubricating oil between heat exchange mechanism and the wall of closed container 8 is formed, be also effective by the outside wall surface of closed container 8 and the mechanism of heat of drawing last breath outward.
Further, the cylinder structure figure of Rotary Compressor of imagination is more than utilized to be illustrated, even if but when compressor modes such as reciprocating, vortexes, as long as the compressor of configurable 2 discharge duct, then same effect can be obtained.
Symbol description:
1: compressor suction line, 3: compressing mechanism, 5: intermediate plate, 6: driving shaft, 7a: minor axis side bearing, 7b: major axis side bearing, 8: closed container, 9: motor, 10: the 1 (downside) compressing mechanism, 11: the 1 (downside) cylinder, 11a: the 1 (downside) cylinder discharge chambe, 15: the 1 (downside) cylinder suction line, 17: the 1 (downside) outlet, 20: the 2 (upside) compressing mechanism, 21: the 2 (upside) cylinder, 21a: the 2 (upside) cylinder discharge chambe, 25: the 2 (upside) cylinder suction line, 27: the 2 (upside) outlet, 30: the 1 discharge paths, silencer is discharged in 31: the 1 (downsides), muffler space is discharged in 32: the 1 (downsides), 33: container, 35: the 1 (downside) discharge duct, 36: heat exchange mechanism, 37: valve, 38: fin, 39: the 1 discharge paths, 40: the 2 discharge paths, silencer is discharged in 41: the 2 (upsides), muffler space is discharged in 42: the 2 (upsides), 43: container, 45: the 2 (upside) discharge duct, 46: be communicated with stream, 47: valve, 50: oil stock portion, 51: oil rotary pump, 52: fuel feed pump, 55: oil surrounds mechanism, 56: oily return loop, 57: oil eliminator, 60: compressing mechanism, 61: compression cylinder, 61a: cylinder discharge chambe, 65: cylinder suction line, 90: closed container base, 70: the 1 discharge paths, 71: the 1 discharge silencer, 72: the 1 discharge muffler space, 73: container, 75: the 1 discharge duct, 76: heat exchange mechanism, 77: valve, 78: fin, 79: the 1 outlets, 80: the 2 discharge paths, 81: the 2 discharge silencer, 82: the 2 discharge muffler space, 83: container, 85: the 2 discharge duct, 87: valve, 89: the 2 outlets, 102: radiator, 103: expansion valve, 104: evaporimeter, 105: refrigerant piping, 110: low-pressure shell type 2 cylinder compressor (coolant compressor, embodiment 1), 120: coolant compressor, 130: utilize fluid circuit, 140: Teat pump hot water supply device (embodiment 2), 210: low-pressure shell type 2 cylinder compressor (coolant compressor, embodiment 3), 220: main refrigerant circuit, 240: heat pump assembly (embodiment 4), 310: low-pressure shell type 2 cylinder compressor (coolant compressor, embodiment 5), 320: main refrigerant circuit, 340: heat pump assembly (embodiment 6), 410: low-pressure shell type 2 cylinder compressor (coolant compressor, embodiment 7), 420: main refrigerant circuit, 440: heat pump assembly (embodiment 8), 510: low-pressure shell type 1 cylinder compressor (coolant compressor, embodiment 9), 540: Teat pump hot water supply device (embodiment 10).

Claims (13)

1. a coolant compressor, is characterized in that: have the closed container of low-pressure shell type, compressing mechanism, motor and oil stock portion;
This compressing mechanism is accommodated in this closed container, sucks and compressed refrigerant;
This motor is accommodated in described closed container, drives described compressing mechanism;
This oil stock portion is formed in the bottom in described closed container, stores lubricating oil;
Described coolant compressor has and is being stored in the mechanism carrying out heat exchange between the lubricating oil in described oil stock portion and the high-pressure refrigerant of discharging from described compressing mechanism.
2. coolant compressor according to claim 1, it is characterized in that: have the 1st discharge path flow through from the high-pressure refrigerant of the 1st compressing mechanism discharge forming described compressing mechanism, the 1st discharge path is guided by the outside to described closed container by described oil stock portion;
Have the 2nd discharge path flow through from the high-pressure refrigerant of the described 2nd compressing mechanism discharge forming described compressing mechanism, the 2nd discharge path is directly guided by the outside to described closed container.
3. coolant compressor according to claim 2, is characterized in that: the stream that described 1st discharge path has through described compressing mechanism with described 2nd discharge path and is communicated with.
4. the coolant compressor according to Claims 2 or 3, is characterized in that: be provided with that the high-pressure refrigerant be just discharged in described 1st compressing mechanism flows into and the be communicated with described 1st discharge path the 1st discharge silencer;
Be provided with that the high-pressure refrigerant be just discharged in described 2nd compressing mechanism flows into and the be communicated with described 2nd discharge path the 2nd discharge silencer;
Described 1st discharge silencer and the described 2nd is discharged silencer and is communicated with.
5. the coolant compressor according to any one of claim 2 to 4, it is characterized in that: on described 1st discharge path and described 2nd discharge path, be respectively equipped with the pressure drag mechanism adjusted refrigerant flow, described cold-producing medium flows respectively in described 1st discharge path and described 2nd discharge path.
6. coolant compressor according to claim 3, is characterized in that: after being assigned to the described stream that described 1st discharge path is communicated with described 2nd discharge path, and the mechanism of described heat exchange is carried out in described 1st discharge path configuration.
7. coolant compressor according to claim 2, is characterized in that: described compressing mechanism is the twin compressor be made up of 2 compression cylinders.
8. coolant compressor according to claim 1, is characterized in that: described closed container possesses the adiabatic mechanism preventing described lubricating oil from externally dispelling the heat from the wall of described closed container.
9. coolant compressor according to claim 1, it is characterized in that: be provided with heat exchange mechanism in a part for the scope by described oil stock portion of described 1st discharge path, between this heat exchange mechanism and the wall of described closed container, configure the oil flowing of described lubricating oil blocked surround mechanism.
10. coolant compressor according to claim 1, is characterized in that: the intermiscibility of described lubricating oil and hydrocarbon refrigerant is little.
11. coolant compressors according to claim 9, is characterized in that: described lubricating oil uses the alkyl diol containing oxirane, with make 40 DEG C, under atmospheric pressure dynamic viscosity for more than 18cSt.
12. coolant compressors according to claim 1, is characterized in that: described compressing mechanism is made up of the 2nd compressing mechanism of the 1st compressing mechanism with the top being configured at the 1st compressing mechanism;
Described coolant compressor has:
The 1st discharge silencer that high-pressure refrigerant after just discharging from described 1st compressing mechanism flows into,
Discharge silencer be communicated with the 1st, by the 1st discharge path that the outside directly to described closed container guides,
The 2nd discharge silencer that high-pressure refrigerant after just discharging from described 2nd compressing mechanism flows into, and
Discharge silencer be communicated with the 2nd, by the 2nd discharge path that the outside directly to described closed container guides, and,
Be stored in the lubricating oil in described oil stock portion and flowing between the described 1st high-pressure refrigerant of discharging in silencer and carry out heat exchange.
13. 1 kinds of heat pump assemblies, use the coolant compressor according to any one of claim 1 to 12.
CN201280073851.8A 2012-05-09 2012-05-09 Refrigerant compressor and heat pump device Expired - Fee Related CN104380009B (en)

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