CN101535646A - Reciprocating compressor of refrigerating machine - Google Patents
Reciprocating compressor of refrigerating machine Download PDFInfo
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- CN101535646A CN101535646A CNA2007800424327A CN200780042432A CN101535646A CN 101535646 A CN101535646 A CN 101535646A CN A2007800424327 A CNA2007800424327 A CN A2007800424327A CN 200780042432 A CN200780042432 A CN 200780042432A CN 101535646 A CN101535646 A CN 101535646A
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- refrigerant
- refrigerating machine
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- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1009—Distribution members
- F04B27/1018—Cylindrical distribution members
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- 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
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1081—Casings, housings
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- 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
- F04B39/06—Cooling; Heating; Prevention of freezing
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- 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
- F04B39/06—Cooling; Heating; Prevention of freezing
- F04B39/062—Cooling by injecting a liquid in the gas to be compressed
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/02—Compression machines, plants or systems with non-reversible cycle with compressor of reciprocating-piston type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
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- 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
- F25B2400/13—Economisers
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- 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
- F25B2400/23—Separators
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Sliding Valves (AREA)
- Compressor (AREA)
Abstract
A reciprocating compressor of refrigerating machine that realizes inhibition of any temperature increase of discharged refrigerant and enhancing of refrigerant compression efficiency. The reciprocating compressor of refrigerating machine is one comprising housing (16) with cylinder bore (30); piston (32) capable of reciprocating motion in the cylinder bore (30), fitted in the cylinder bore (30); intermediate pressure chamber (68) disposed within the housing (16), into which a low-temperature refrigerant is led from gas-liquid separator (10) of refrigerating machine; and rotary valve (78) disposed between compression chamber (33) and the intermediate pressure chamber (68), wherein the rotary valve (78) rotates in conjunction with main shaft (34) of the compressor and, when the refrigerant is in the stage of compression within the compression chamber (33), opens so as to jet the low-temperature refrigerant from the intermediate pressure chamber (68) into the compression chamber (33).
Description
Technical field
The present invention relates to a kind of reciprocal compressor of refrigerating machine, relate in particular to the compressor of the included refrigerating machine of the air-conditioning system that is applicable to automobile.
Background technique
This reciprocal compressor comprises: have a plurality of cylinder thoraxes cylinder body, can be free to-and-fro motion ground insert each cylinder thorax of cylinder body respectively and in the cylinder thorax, form the piston of pressing chamber and for making each piston rotatable main shaft of to-and-fro motion in the cylinder thorax of correspondence.When making main axis rotation, the to-and-fro motion successively in the cylinder thorax of correspondence of each piston, the to-and-fro motion of such piston make that being inhaled in the corresponding pressing chamber refrigeration agent from refrigeration agent compresses, discharges this a succession of process again to compressed refrigerant from pressing chamber and carry out (patent documentation 1) repeatedly in pressing chamber.
Patent documentation 1: the Japan Patent spy opens communique 2001-No. 027177
The air-conditioning system of automobile, be the general replacement Freon gas that is called R134a that uses of refrigeration agent of its refrigerating machine.Yet such replacement Freon gas has the very high terrestrial climate coefficient (Global Warming Potential=GWP) that warms, and particularly, replaces the GWP of Freon gas to be about 1300.
Therefore, the refrigerating machine in the patent documentation 1 uses the lower carbon dioxide (CO of GWP
2) replace above-mentioned replacement Freon gas as refrigeration agent.In addition, in recent years, also propose to use the lower new replacement refrigeration agent of GPW, this replacements refrigeration agent contains pair keys (for example R1234YF etc.).
At CO
2Refrigeration agent when being compressed by compressor, the temperature of this refrigeration agent, be the discharge temperature of refrigeration agent height when being compressed by compressor than R134a.Particularly, CO
2The discharge temperature of refrigeration agent surpasses 150 ℃, and the thermal load that compressor is subjected to is bigger.On the other hand, when above-mentioned new replacement refrigeration agent is compressed by compressor, the discharge temperature of this refrigeration agent identical degree when being suppressed in R134a.Yet new replacement refrigeration agent its pair key under the service condition of high temperature that contains two keys disconnects easily, therefore decomposes easily under the discharge temperature of refrigeration agent.
Summary of the invention
The object of the present invention is to provide a kind of reciprocal compressor of refrigerating machine of the compression efficiency that when the discharge temperature that suppresses refrigeration agent rises, can improve refrigeration agent.
The technological scheme that the technical solution problem is adopted
To achieve these goals, the reciprocal compressor of refrigerating machine of the present invention comprises: shell, piston, and gatherer, above-mentioned shell has the cylinder thorax, above-mentioned piston is entrenched in the above-mentioned cylinder thorax for form pressing chamber in above-mentioned cylinder thorax, and can to-and-fro motion in the cylinder thorax, by its to-and-fro motion, comprise in pressing chamber and suck refrigeration agent, refrigeration agent compresses and discharge compressed refrigerant in interior a succession of process from pressing chamber to sucking in pressing chamber, discharging refrigerant is supplied with towards the refrigerant cycle path of refrigerating machine, above-mentioned gatherer configuration in the enclosure, when refrigeration agent is in compression process in pressing chamber, above-mentioned gatherer imports in the pressing chamber intermediate refrigerant in specified time limit from the refrigerant cycle path, intermediate refrigerant has the high pressure of pressure of the compressed refrigerant more indoor than compression.
Comparatively it is desirable to, the intermediate refrigerant that gatherer will have the temperature lower than the temperature of the compressed refrigerant that is in compression process imports pressing chamber.
Particularly, gatherer comprises: intermediate pressure chamber, connecting path and valve, above-mentioned intermediate pressure chamber forms in the enclosure, intermediate refrigerant is supplied with towards it from the refrigerant cycle path, said connecting path is connected above-mentioned intermediate pressure chamber with pressing chamber, above-mentioned valve is arranged on the said connecting path, connecting path is opened and closed, in the time-domain till the pressure that is in the compressed refrigerant of compression process in pressing chamber reaches the pressure of the indoor intermediate refrigerant of intermediate pressure connecting path is opened.
Adopt above-mentioned reciprocal compressor, when refrigeration agent was in compression process in pressing chamber, valve was opened.In the moment that valve is opened, the pressure height of the compressed refrigerant in the pressure ratio pressing chamber of the intermediate refrigerant that intermediate pressure is indoor, therefore, when valve was opened, intermediate medium was sprayed in pressing chamber.At this moment, the temperature of the compressed refrigerant that the temperature of intermediate refrigerant is interior than the pressing chamber that is in compression process is low, and the compressed refrigerant in the pressing chamber is cooled because of mixing with intermediate refrigerant.
Therefore, can suppress as refrigeration agent, can use carbon dioxide and the refrigeration agent that comprises compound with above-mentioned pair of key from the temperature rising of the refrigeration agent of compressor discharge, helpful to preventing that terrestrial climate from warming.In addition, when refrigeration agent is in compression process in pressing chamber,, then can improve the compression efficiency of compressed refrigerant, can increase substantially the energy efficiency of refrigerating machine if spray intermediate refrigerant towards pressing chamber.
Above-mentioned valve be mechanically combine with main shaft and with the rotary valve of integrated spindle axis rotation, or the rotary valve that rotates of the effect of the motor by being independent of main shaft, or solenoid valve.
In addition, compressor can also comprise the varying capacity mechanism of the discharge capacity that can change compressed refrigerant, and this varying capacity mechanism has swash plate.
Description of drawings
Fig. 1 is the figure of the summary of expression refrigerating machine.
Fig. 2 is the sectional view of details of the compressor of presentation graphs 1.
Fig. 3 is the figure of the rotary valve of expression variation.
Fig. 4 is the figure of expression electromagnetic opening and closing valve.
Embodiment
The refrigerating machine of Fig. 1 is installed in the automobile-used air-conditioning system, comprises the circulating path 2 that refrigeration agent is used.On this circulating path 2, insert compressor 4, condenser 6, first expansion valve 8, gas-liquid separator 10, second expansion valve 12 and vaporizer 14 successively.Compressor 4 is discharged refrigeration agent compression back, and the refrigeration agent that is discharged from is supplied with towards condenser 6, circulation in circulating path 2.
Herein, circulating path 2 has from the discharge port 4d of compressor 4 and arrives the high-pressure area 2H of first expansion valve 8 and the area of low pressure 2L that arrives the inhalation port 4s of compressors 4 from first expansion valve 8 via gas-liquid separator 10, second expansion valve 12 and vaporizer 14 via condenser 6.
Fig. 2 represents the details of compressor 4.
In addition, dispose compression unit 28 in middle casing 20, compression unit 28 is elaborated below.
On the other hand, in crank chamber 24, dispose main shaft 34.This main shaft 34 is located with the axis coaxle shape of cylinder body 26, has the inner and outer end respectively.The inner of main shaft 34 enters in the cylinder body 26, can be supported by cylinder body 26 by bearing 36 with rotating freely.On the other hand, the outer end of main shaft 34 projects to the outside of shell 16.That is, main shaft 34 runs through end plate 18, is supported by end plate 18 by bearing 38 and sealing unit 40.The outer end of main shaft 34 is connected with the motor of automobile by power transfer path (not shown).Therefore, when motor was passed to main shaft 34, main shaft 34 rotated towards a direction in the driving force of motor.
In addition, dispose swash plate 46 in crank chamber 24, this swash plate 46 is around main shaft 34.Swash plate 46 and rotor 42 are connected to each other by connecting rod 48, and this connecting rod 48 allows swash plate 46 to fascinate with respect to main shaft 34 for the angle of inclination may that makes swash plate 46.In addition, supporting wobble plate 42 by radial bearing 50 and thrust-bearing 52 on swash plate 46, the rotation of wobble plate 54 is stoped mechanism (not shown) to stop by rotation.
Above-mentioned wobble plate 54 links with each piston 32 respectively by piston rod 56, and these piston rods 56 have spherojoint 57a, 57b on its two ends.Spherojoint 57a links wobble plate 54 and piston rod 56, and spherojoint 57b links piston rod 56 and piston 32.Therefore, when making main shaft 34 rotations, the rotation of main shaft 34 is transformed into the to-and-fro motion of each piston 32 by rotor 42, swash plate 46, wobble plate 54 and piston rod 56.
As can be seen from Figure 2, between cylinder body 26 and cylinder cap 22, accompany valve plate 58 by packing ring (not shown).On this valve plate 58, have distribute to each cylinder thorax 30 respectively, be the inlet hole 60 and the tap hole 62 of pressing chamber 33.
On the other hand, be formed with suction chamber 64 between valve plate 58 and cylinder cap 22, discharge chamber 66 and intermediate pressure chamber 68, these chambers 64,66,68 are independently of one another.More specifically, intermediate pressure chamber 68 is configured in the central authorities of cylinder cap 22, discharge chamber 66 and be the ring-type around intermediate pressure chamber 68, and suction chamber 64 is for centering on the ring-type of discharging chamber 66.That is, intermediate pressure chamber 68, discharge chamber 66 and suction chamber 64 are triple structures.
Above-mentioned inlet hole 60 is assigned suction valve 70 respectively, and these suction valves 70 can open and close the inhalation port 60 of correspondence.In addition, tap hole 62 is assigned expulsion valve 72 respectively, these expulsion valves 72 can open and close the tap hole 62 of correspondence.Suction valve 70 and expulsion valve 72 form by leaf valve.Suction valve 70 is configured in leaning on the end face of pressing chamber 33 sides of valve plate 58, and relative therewith, expulsion valve 72 is configured on the other end of valve plate 58.In addition, among Fig. 2, reference marks 73 expression is used to limit the valve retainer of the opening action of expulsion valve 72.
In addition, on cylinder cap 22, be formed with importing port 74.This importing port 74 is communicated with above-mentioned intermediate pressure chamber 68, on the other hand, is connected with lead-in path 76.Can be clear and definite from Fig. 1, this lead-in path 76 is connected with above-mentioned gas-liquid separator 10.Such lead-in path 76 makes the intermediate refrigerant of gaseous state import in the intermediate pressure chamber 68 via importing port 74 from gas-liquid separator 10.
On the other hand, dispose rotary valve 78 between intermediate pressure chamber 68 and main shaft 34, this rotary valve 78 is a cylindrical shape, can be supported on the cylinder body 26 with rotating freely.That is, be formed with the cylinder hole 79 that holds rotary valve 78 on cylinder body 26, rotary valve 78 is entrenched in this cylinder hole 79 airtightly.
Be formed with valve path 86 in rotary valve 78, this valve path 86 has: at the valve port 86a of the outer circumferential face opening of rotary valve 78 and the connecting port 86b that is communicated with intermediate pressure chamber 68.As can be seen from Figure 2, valve port 86a be positioned in above-mentioned valve plate 58 an end face near.
In addition, be formed with a plurality of attachment holes 88 in cylinder body 26, these attachment holes 88 dispose accordingly with pressing chamber 33 respectively.More specifically, each attachment hole 88 is radial holes, and the pressing chamber 33 from the inner peripheral surface in above-mentioned cylinder hole 79 towards correspondence extends, and has: near an end face of valve plate 58 towards the outer end of pressing chamber 33 openings and in the inner of the inner peripheral surface upper shed in cylinder hole 79.Regardless of the to-and-fro motion of piston 32, the outer end of each attachment hole 88 connects all the time with corresponding pressing chamber 33.Relative therewith, the inner of each attachment hole 88 rotary valve 78 circumferentially on equally spaced configuration, when making rotary valve 78 rotations, be connected off and on the valve port 86a of valve path 86.That is on the rotating locus that forms by valve port 86a when, the inner of attachment hole 88 is configured in rotary valve 78 rotations.
Therefore, when rotary valve 78 was rotated with main shaft 34, the valve port 86a of valve path 88 was connected successively with the attachment hole 88 of each pressing chamber 33.This means in the rotation of rotary valve 78, intermediate pressure chamber 68 connects by rotary valve 78 successively with respect to each pressing chamber 33, and rotary valve 78 is the distributing valves that open and close each attachment hole 88 successively, the intermediate refrigerant in the intermediate pressure chamber 68 are distributed to each pressing chamber 33.Herein, 33 distribution that distribute will become clear and definite by explanation described later to intermediate refrigerant constantly and between allotment period from middle pressure chamber 68 towards pressing chamber.
When making main shaft 34 rotations as described above, the to-and-fro motion successively in the cylinder thorax 30 of correspondence of each piston 32.Therefore, the refrigeration agent in the suction chamber 64 is inhaled in each pressing chamber 33 via suction valve 70 and inlet hole 60.Afterwards, in each pressing chamber 33, the refrigeration agent that is inhaled into is compressed, and then, this compressed refrigerant is discharged towards discharging chamber 66 via tap hole 62 and expulsion valve 72 from pressing chamber 33.Be connected with the high-pressure area 2H of circulating path 2 owing to discharge chamber 66, so discharging refrigerant 6 supplies from compressor 2 towards condenser.On the other hand, because suction chamber 64 is connected with the area of low pressure 2L of circulating path 2, therefore the refrigeration agent that returns from vaporizer 14 is inhaled into pressing chamber 33 from suction chamber 64.
On the other hand, rotary valve 78 and the rotation of main shaft 34 one, the valve port 86a of the valve path 86 of rotary valve 78 only are connected with attachment hole 88 that refrigeration agent is in the pressing chamber 33 of compression process constantly with between allotment period in above-mentioned distribution.That is, rotary valve 78 is distributing the moment to open, and close the finish time during distribution.Herein, distribute constantly and be set in respectively between allotment period in the time-domain till the pressure that is in the refrigeration agent of compression process in the pressing chamber 33 rises to the pressure of the intermediate refrigerant in the intermediate pressure chamber 68.
Therefore, in the compression process of refrigeration agent, when rotary valve 78 was opened, the intermediate refrigerant in the intermediate pressure chamber 68 was via rotary valve 78 and is connected 88 towards pressing chamber 33 interior injections.Herein, the intermediate refrigerant of gas phase imports in intermediate pressure chamber 68 via lead-in path 76 from above-mentioned gas-liquid separator 10.Therefore, the intermediate refrigerant in the intermediate pressure chamber 68, the intermediate refrigerant of promptly spraying in the pressing chamber 33 have recently from the much lower temperature of the discharge temperature of the discharging refrigerant of compressor 4 with than the low pressure of head pressure of discharging from compressor 4.Consequently, towards the intermediate refrigerant and the refrigerant mixed that is in the high temperature of compression process of the pressing chamber 33 interior low temperature that spray, therefore, the compressed refrigerants in the pressing chamber 33 are cooled, and thus, can suppress the temperature rising from the discharging refrigerant of compressor 4.
If limiting the temperature of discharging refrigerant like this rises, even what then refrigeration agent used is carbon dioxide, also can reduce the thermal load that acts on compressor 4 significantly, in addition, even if for example refrigeration agent uses R1234YF etc. to contain the new refrigerant of two keys of hydrocarbon, its pair key can not decompose yet.Therefore, compressor 4 of the present invention can use and prevent terrestrial climate comparatively desirable refrigeration agent aspect warming, is being carbon dioxide and above-mentioned new refrigeration agent.
In addition,, then can improve the compression efficiency of the refrigeration agent in the pressing chamber 33, can improve the energy efficiency of refrigerating machine tremendously if in pressing chamber 33, spray refrigerant of low temperature as described above.That is, can easily realize the multiple-effect circulation that this refrigerating machine is pursued.
On the other hand, above-mentioned crank chamber 24 is connected respectively with discharge chamber 66 with suction chamber 64 by the connecting path 96,98 shown in the dot and dash line among Fig. 2, and these connecting paths 96,98 run through valve plate 58 and cylinder body 26 respectively.On connecting path 96, dispose throttle valve 100, on the other hand, on connecting path 98, dispose solenoid electric valve 102.These solenoid electric valve 102 controls should flow into the influx of the high-pressure refrigerant of crank chamber 24 from discharge chamber 66, adjust the pressure in the crank chamber 24.
The inclination angle of above-mentioned swash plate 46 act on by each piston 32 swash plate 46 front surface compression reaction force and act on pressure in the crank chamber 24 at the back side of swash plate 46, be that back pressure decides, therefore change by the pressure of adjusting in the crank chamber 24.In addition, because the inclination angle of swash plate 46 determines the stroke of each piston 32, therefore can change according to the variation at the inclination angle of swash plate 46 from the discharge capacity of the refrigeration agent of compressor 4.
Because the attachment hole 86 of above-mentioned pressing chamber 33 is configured near the top dead center of piston 32, even therefore the stroke of piston 32 changes, rotary valve 78 can not change constantly and between allotment period with respect to the distribution of each pressing chamber 33 yet.Therefore, stroke regardless of piston 32, relation between the pressure of the intermediate refrigerant in the pressure of the refrigeration agent of discharging from compressor 4 and the intermediate pressure chamber 68 all keeps roughly certain, in the compression process of refrigeration agent, can be stably in the pressing chamber 33 intermediate refrigerant of injection low temperature.
The present invention is not limited by an above-mentioned embodiment, can carry out various distortion.
For example, Fig. 3 represents to be independent of the rotary valve 78 that main shaft 34 is rotated.In this case, rotary valve 78 links with the output shaft 92 of motor 90, and motor 90 is installed on the outer surface of cylinder cap 22.Usually, motor 90 synchronously makes rotary valve 78 rotations with the rotation of main shaft 34, but also can adjust as required between the distribution moment and allotment period of rotary valve 78.
Fig. 4 represents to replace the electromagnetic opening and closing valve 94 that rotary valve 78 uses.Electromagnetic opening and closing valve 94 disposes accordingly with each pressing chamber 33, performance and above-mentioned rotary valve 78 identical functions.
In addition, reciprocal compressor of the present invention also can be the compressor of constant volume formula, also can replace motor with motor and drive.In addition, reciprocating form also is not limited to illustrated oscillation plate type, also can be board-like and other axial piston mode of monocline.
Claims (9)
1. the reciprocal compressor of a refrigerating machine is characterized in that, comprising:
Shell, this shell has the cylinder thorax;
Piston, this piston is entrenched in the described cylinder thorax in order to form pressing chamber in described cylinder thorax, and can to-and-fro motion in described cylinder thorax, by its to-and-fro motion, comprise in described pressing chamber sucking refrigeration agent, in described pressing chamber, the suction refrigeration agent is compressed and discharging compressed refrigerant in interior a succession of process, described discharging refrigerant is supplied with towards the refrigerant cycle path of refrigerating machine from described pressing chamber; And
Gatherer, this gatherer is configured in the described shell, when refrigeration agent is in compression process in described pressing chamber, described gatherer makes intermediate refrigerant import in specified time limit in the described pressing chamber from described refrigerant cycle path, and described intermediate refrigerant has the pressure higher than the pressure of the compressed refrigerant in the described pressing chamber.
2. the reciprocal compressor of refrigerating machine as claimed in claim 1 is characterized in that, the described intermediate refrigerant that described gatherer will have the temperature lower than the temperature of the described compressed refrigerant that is in described compression process imports in the described pressing chamber.
3. the reciprocal compressor of refrigerating machine as claimed in claim 1 is characterized in that,
Described gatherer comprises:
Intermediate pressure chamber, this intermediate pressure chamber are formed in the described shell, and described intermediate refrigerant is supplied with towards described intermediate pressure chamber from described refrigerant cycle path;
Connecting path, this connecting path is connected described intermediate pressure chamber with described pressing chamber; And
Valve, this valve is arranged on the described connecting path, described connecting path is opened and closed, in the time-domain till the pressure that is in the described compressed refrigerant of compression process in described pressing chamber reaches the pressure of the indoor described intermediate refrigerant of described intermediate pressure described connecting path is opened.
4. the reciprocal compressor of refrigerating machine as claimed in claim 3 is characterized in that, described valve be mechanically combine with described main shaft and with the rotary valve of described integrated spindle axis rotation.
5. the reciprocal compressor of refrigerating machine as claimed in claim 3 is characterized in that, described valve is the rotary valve that rotates by the effect of the motor that is independent of described main shaft.
6. the reciprocal compressor of refrigerating machine as claimed in claim 3 is characterized in that, described valve is a solenoid valve.
7. the reciprocal compressor of refrigerating machine as claimed in claim 1 is characterized in that, also comprises the varying capacity mechanism of the discharge capacity that can change compressed refrigerant, and this varying capacity mechanism has swash plate.
8. the reciprocal compressor of refrigerating machine as claimed in claim 1 is characterized in that, refrigeration agent is a carbon dioxide.
9. the reciprocal compressor of refrigerating machine as claimed in claim 1 is characterized in that, refrigeration agent comprises the compound of the two keys with hydrocarbon.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006325544A JP5118340B2 (en) | 2006-12-01 | 2006-12-01 | Reciprocating compressor for refrigeration circuit |
| JP325544/2006 | 2006-12-01 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101535646A true CN101535646A (en) | 2009-09-16 |
Family
ID=39467942
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007800424327A Pending CN101535646A (en) | 2006-12-01 | 2007-11-30 | Reciprocating compressor of refrigerating machine |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20100068085A1 (en) |
| EP (1) | EP2088322A4 (en) |
| JP (1) | JP5118340B2 (en) |
| CN (1) | CN101535646A (en) |
| WO (1) | WO2008066156A1 (en) |
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| CN102235775A (en) * | 2010-04-23 | 2011-11-09 | Lg电子株式会社 | Heat pump type speed heating apparatus |
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| CN110318971A (en) * | 2018-03-30 | 2019-10-11 | 株式会社丰田自动织机 | Piston compressor |
| CN112129000A (en) * | 2019-06-24 | 2020-12-25 | 杭州三花研究院有限公司 | Thermal management system |
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| JP5400043B2 (en) * | 2008-06-16 | 2014-01-29 | 三菱電機株式会社 | Scroll compressor |
| JP5294719B2 (en) * | 2008-06-17 | 2013-09-18 | 三菱電機株式会社 | Rotary compressor |
| JPWO2009157320A1 (en) * | 2008-06-24 | 2011-12-08 | 三菱電機株式会社 | Refrigeration cycle apparatus and air conditioner |
| JP2010019457A (en) * | 2008-07-09 | 2010-01-28 | Sanden Corp | Refrigerating circuit |
| JP5062160B2 (en) * | 2008-12-19 | 2012-10-31 | 株式会社デンソー | Refrigeration cycle and compressor |
| JP6192806B2 (en) * | 2014-03-17 | 2017-09-06 | 三菱電機株式会社 | Refrigeration equipment |
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| JPS5749083A (en) * | 1980-09-10 | 1982-03-20 | Hitachi Ltd | Reciprocating compressor |
| JPS5815776A (en) * | 1981-07-21 | 1983-01-29 | Toshiba Corp | Injection device of reciprocating compressor |
| JPS59131984U (en) * | 1983-02-25 | 1984-09-04 | 三菱重工業株式会社 | compressor |
| JP2616295B2 (en) * | 1991-09-02 | 1997-06-04 | 株式会社豊田自動織機製作所 | Swash plate compressor for refrigeration equipment |
| JP2000145641A (en) * | 1998-11-06 | 2000-05-26 | Sanden Corp | Reciprocating compressor |
| JP2001027177A (en) | 1999-07-15 | 2001-01-30 | Zexel Valeo Climate Control Corp | Variable displacement swash plate type compressor |
| JP4385516B2 (en) * | 2000-11-07 | 2009-12-16 | 株式会社豊田自動織機 | Piston compressor |
| JP2002228289A (en) * | 2000-11-30 | 2002-08-14 | Aisin Seiki Co Ltd | Rotary valve unit and pulse pipe refrigerating machine |
| JP2004176543A (en) * | 2002-11-22 | 2004-06-24 | Sanden Corp | Compressor |
| JP2004183605A (en) * | 2002-12-05 | 2004-07-02 | Sanden Corp | Electric compressor |
| JP3789898B2 (en) * | 2003-03-17 | 2006-06-28 | 東芝キヤリア株式会社 | Refrigerant, refrigerant compressor and refrigeration apparatus |
| RU2007146973A (en) * | 2005-05-18 | 2009-06-27 | Е.И.Дюпон де Немур энд Компани (US) | HYBRID VAPOR COMPRESSION-ABSORPTION CYCLE |
-
2006
- 2006-12-01 JP JP2006325544A patent/JP5118340B2/en not_active Expired - Fee Related
-
2007
- 2007-11-30 WO PCT/JP2007/073169 patent/WO2008066156A1/en active Application Filing
- 2007-11-30 CN CNA2007800424327A patent/CN101535646A/en active Pending
- 2007-11-30 EP EP07849947A patent/EP2088322A4/en not_active Withdrawn
- 2007-11-30 US US12/516,718 patent/US20100068085A1/en not_active Abandoned
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102235777A (en) * | 2010-04-22 | 2011-11-09 | Lg电子株式会社 | Heat pump type speed heating apparatus |
| CN102235777B (en) * | 2010-04-22 | 2014-07-16 | Lg电子株式会社 | Heat pump type speed heating apparatus |
| CN102235775A (en) * | 2010-04-23 | 2011-11-09 | Lg电子株式会社 | Heat pump type speed heating apparatus |
| CN102235775B (en) * | 2010-04-23 | 2014-06-18 | Lg电子株式会社 | Heat pump type speed heating apparatus |
| US8850837B2 (en) | 2010-04-23 | 2014-10-07 | Lg Electronics Inc. | Heat pump type speed heating apparatus |
| CN106352100A (en) * | 2015-07-17 | 2017-01-25 | 株式会社鹭宫制作所 | Pressure operating valve and frozen cycle |
| CN106352100B (en) * | 2015-07-17 | 2019-02-01 | 株式会社鹭宫制作所 | Pressure-operated valve and refrigerating circulation system |
| CN110318971A (en) * | 2018-03-30 | 2019-10-11 | 株式会社丰田自动织机 | Piston compressor |
| CN109958597A (en) * | 2019-03-12 | 2019-07-02 | 复盛实业(上海)有限公司 | A kind of compressed air unit and its heat-exchange system |
| CN112129000A (en) * | 2019-06-24 | 2020-12-25 | 杭州三花研究院有限公司 | Thermal management system |
Also Published As
| Publication number | Publication date |
|---|---|
| US20100068085A1 (en) | 2010-03-18 |
| JP5118340B2 (en) | 2013-01-16 |
| EP2088322A1 (en) | 2009-08-12 |
| EP2088322A4 (en) | 2009-12-30 |
| JP2008138589A (en) | 2008-06-19 |
| WO2008066156A1 (en) | 2008-06-05 |
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Open date: 20090916 |