CN101925743A - Compressor - Google Patents

Compressor Download PDF

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Publication number
CN101925743A
CN101925743A CN200980103011XA CN200980103011A CN101925743A CN 101925743 A CN101925743 A CN 101925743A CN 200980103011X A CN200980103011X A CN 200980103011XA CN 200980103011 A CN200980103011 A CN 200980103011A CN 101925743 A CN101925743 A CN 101925743A
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CN
China
Prior art keywords
chamber
component parts
roller
blade
piston
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Granted
Application number
CN200980103011XA
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Chinese (zh)
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CN101925743B (en
Inventor
小川步
足立诚
西本康伸
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication of CN101925743A publication Critical patent/CN101925743A/en
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Publication of CN101925743B publication Critical patent/CN101925743B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/32—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members
    • F04C18/322—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movement defined in group F04C18/02 and relative reciprocation between the co-operating members with vanes hinged to the outer member and reciprocating with respect to the outer member
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/263—HFO1234YF

Abstract

A compressor in which performance degradation caused by inflow of high-temperature lubricating oil into a low-pressure chamber does not occur. A piston (62) is placed in a cylinder chamber (71), and a refrigerant flowing into the cylinder chamber is compressed when the piston (62) moves in the cylinder chamber. The piston (62) is constructed from two piston forming members (81, 82) stacked in the vertical direction (axis direction of the cylinder).The piston forming members (81, 82) respectively have roller forming sections (81a, 82a) having an annular shape and moving along the side wall surface of the cylinder chamber while being in contact with the side wall surface to partition the cylinder chamber into a high-pressure chamber and a low-pressure chamber and to change the volumes of the high-pressure chamber and the low-pressure chamber. The piston forming members (81, 82) also respectively have blade forming sections (81b, 82b) formed integrally with the roller forming sections (81a, 82a) and partitioning, together with the roller forming sections (81a, 82a), the cylinder chamber into the high-pressure chamber and the low-pressure chamber.

Description

Compressor
Technical field
The present invention relates to a kind of compressor of compression refrigerant.
Background technique
In the compressor of record, the internal configurations in the cylinder chamber of the inside that is formed at cylinder body is formed with the piston of roller and blade in patent documentation 1, by piston the cylinder chamber is divided into suction chamber (low pressure chamber) and sprays chamber (hyperbaric chamber).And, move along this side wall surface in the time of side wall surface by roller butt cylinder chamber, thus the volume-variation of ejection chamber and compress the indoor refrigerant of ejection.
Patent documentation 1: the Japan Patent spy opens the 2004-124948 communique
At this, in patent documentation 1, in the compressor of record, hinder it to move with the contacting of last lower wall surface of cylinder chamber in order to prevent piston, piston (roller and blade) is lower than cylinder chamber height.In addition, because roller is lower than cylinder chamber height, so via the gap of the last lower wall surface of roller and cylinder chamber, the lubricant oil inflow low pressure chamber of the inboard of the roller of flowing through.But, when for a long time, cause the temperature of the refrigerant in the low pressure chamber to rise by this lubricant oil from the quantitative change of the lubricant oil of the interior side inflow low pressure chamber of roller, the performance of compressor reduces.
In addition, because blade is lower than cylinder chamber height, so via the gap of the last lower wall surface of blade and cylinder chamber, lubricant oil flows into low pressure chamber from the hyperbaric chamber.At this, owing to carry out the compression of refrigerant in the hyperbaric chamber, so the temperature in hyperbaric chamber uprises, thus, the temperature of the lubricant oil in the hyperbaric chamber also uprises.Therefore, when the quantitative change of the lubricant oil that flows into low pressure chamber from the hyperbaric chamber for a long time, the temperature of the refrigerant in the low pressure chamber rises, the performance of compressor reduces.
Summary of the invention
The present invention is in view of the above problems and research and development, and its purpose is to provide a kind of amount of the above-mentioned lubricant oil that flows into low pressure chamber few, the compressor that performance can not reduce.
The compressor of first invention is characterized in that having: cylinder body, and it is configured in the confined space, and is provided with the cylinder chamber in inside; The roller of ring-type, it is configured in the inside of described cylinder chamber, the side wall surface of the described cylinder of its outer circumferential face butt chamber and moving along this side wall surface, described cylinder chamber is divided into the compression of carrying out refrigerant and with compressed refrigerant to hyperbaric chamber that described confined space is discharged with import the low pressure chamber of refrigerant from the outside, and make the volume-variation of described hyperbaric chamber and described low pressure chamber; And blade, it is configured in the inside of described cylinder chamber, with described roller described cylinder chamber is divided into described hyperbaric chamber and described low pressure chamber, described roller by described cylinder body axially on stacked a plurality of roller component parts constitute.
In this compressor, since by cylinder body axially on stacked a plurality of roller component parts constitute roller, so in the driving of compressor, between the roller component parts, form the oil film of lubricant oil, between the roller component parts, can form the gap, in roller component parts and the cylinder chamber about the size in the gap between the axial two side walls of cylinder body and the size in the gap between the roller component parts, the gap in roller under the situation about constituting by parts such as roller shown in the past and the cylinder chamber between the axial two side walls of cylinder body slight greatly.On the other hand, the amount of liquid that flows into the gap from hydromechanical viewpoint as can be known under the identical situation of the total of the size in gap, a, gap many more big slight then few more when the quantity in gap.
Therefore, in roller component parts and the cylinder chamber in the total of the size in the size in the gap between the axial two side walls of cylinder body and the gap between the roller component parts, even with identical, also can reduce the amount of the lubricant oil that flows into low pressure chamber as constituting in roller under the situation of roller and the cylinder chamber in the total of the size in the gap of the axial two side walls of cylinder body by parts shown in the past.
Perhaps, flow under the situation of the amount of the lubricant oil in the low pressure chamber and same degree in the past, can make in roller component parts and the cylinder chamber total in the size in the size in the gap between the axial two side walls of cylinder body and the gap between the roller component parts, big such as the size in the gap of the axial two side walls of cylinder body in roller under the situation about roller being made of parts shown in the past and the cylinder chamber, can prevent reliably that the roller component parts from touching in the cylinder chamber the axial two side walls at cylinder body.
In addition, in this compressor, can between the roller component parts, form the amount in gap, distance about the axial two side walls of cylinder body is shortened, not but not equal according to the linear expansion amount of deformation of cylinder body and piston, when in the cylinder chamber in the axial two side walls of cylinder body during near the roller component parts, oil film is pressed off, thereby the gap smaller between the roller component parts, so compare with situation in the past, roller can not contact in the cylinder chamber wall in the axial both sides of cylinder body easily yet.
The compressor of second invention on the basis of compressor of first invention, is characterized in that, by described cylinder body axially on stacked a plurality of blade component parts constitute.
In this compressor, owing to constitute blade by stacked a plurality of blade component parts, so can and the blade component parts between form the oil film of lubricant oil, can between the blade component parts, form the gap, the gap in blade under the situation about constituting by parts such as blade shown in the past about the size in the size in the gap between the axial two side walls of cylinder body and the gap between the blade component parts in blade component parts and the cylinder chamber and the cylinder chamber between the axial two side walls of cylinder body slight greatly.
Therefore, even in blade component parts and the cylinder chamber in the total of the size in the size in the gap between the axial two side walls of cylinder body and the gap between the blade component parts, identical with the total in the size in the gap of the axial two side walls of cylinder body in blade under situation about blade being made of parts shown in the past and the cylinder chamber, also can reduce the amount that flows into the lubricant oil of low pressure chamber from the hyperbaric chamber.
Perhaps, flow into from the hyperbaric chamber under the situation of the amount of the lubricant oil in the low pressure chamber and same degree in the past, can make the total of the size in the size in the gap between the last lower wall surface of blade component parts and cylinder chamber and the gap between the blade component parts, big such as the total in the size in the gap of the axial two side walls of cylinder body in blade under the situation about blade being made of parts shown in the past and the cylinder chamber, can prevent reliably that the blade component parts from touching in the cylinder chamber the axial two side walls at cylinder body.
In addition, under the situation that blade is made of parts, can produce in the central part heat build-up of blades height direction burn sticking, but in this compressor, owing to form blade by stacked a plurality of blade component parts, so the Clearance Flow lubricant oil between the blade component parts, it is sticking to be difficult to generate above-mentioned burning.
In addition, in this compressor, can between the blade component parts, form the amount in gap, distance in the axial two side walls of cylinder body is shortened, not but not equal according to the linear expansion amount of deformation of cylinder body and piston, when in the cylinder chamber in the axial two side walls of cylinder body during near the blade component parts, oil film is pressed off, thereby the gap smaller between the blade component parts, so compare with situation in the past, blade can not contact in the cylinder chamber wall in the axial both sides of cylinder body easily yet.
The compressor of the 3rd invention is characterized in that having: cylinder body, and it is configured in the confined space, and is provided with the cylinder chamber in inside; The roller of ring-type, it is configured in the inside of described cylinder chamber, the side wall surface of the described cylinder of its outer circumferential face butt chamber and moving along this side wall surface, described cylinder chamber is divided into the compression of carrying out refrigerant and with compressed refrigerant to hyperbaric chamber that described confined space is discharged with import the low pressure chamber of refrigerant from the outside, and make the volume-variation of described hyperbaric chamber and described low pressure chamber; And blade, it is configured in the inside of described cylinder chamber, with described roller described cylinder chamber is divided into described hyperbaric chamber and described low pressure chamber, described blade by described cylinder body axially on stacked a plurality of blade component parts constitute.
In this compressor, can access the same effect of compressor with second invention.
The compressor of the 4th invention is characterized in that having: cylinder body, and it is configured in the confined space, and is provided with the cylinder chamber in inside; And piston, it is configured in the inside of described cylinder chamber, described piston has: the roller of ring-type, the side wall surface of the described cylinder of its outer circumferential face butt chamber and moving along this side wall surface, described cylinder chamber is divided into the compression of carrying out refrigerant and with compressed refrigerant to hyperbaric chamber that described confined space is discharged with import the low pressure chamber of refrigerant from the outside, and make the volume-variation of described hyperbaric chamber and described low pressure chamber; And, blade, itself and described roller are integrally formed, with described roller described cylinder chamber are divided into described hyperbaric chamber and described low pressure chamber, and, by described cylinder body axially on stacked a plurality of piston component parts constitute.
In this compressor, since the piston of integrally formed roller and blade by cylinder body axially on stacked a plurality of piston component parts constitute, so can access the identical effect of compressor with first to the 3rd invention, and because integrally formed roller and blade, produce burning so can prevent both from sliding sticking.
(invention effect)
As mentioned above, according to the present invention, can access following effect.
In first invention, even the roller component parts with in the cylinder chamber in the total of the size in the size in the gap between the axial two side walls of cylinder body and the gap between the roller component parts and roller under the situation that constituted roller shown in the past by parts and cylinder chamber the total in the size in the gap of the axial two side walls of cylinder body identical, also can reduce the amount of the lubricant oil that flows into low pressure chamber.
Perhaps, in first invention, flow under the situation of the amount of the lubricant oil in the low pressure chamber and same degree in the past, can make in roller component parts and the cylinder chamber total in the size in the size in the gap between the axial two side walls of cylinder body and the gap between the roller component parts, big such as the size in the gap of the axial two side walls of cylinder body in roller under the situation about roller being made of parts shown in the past and the cylinder chamber, can prevent reliably that the roller component parts from touching in the cylinder chamber the axial two side walls about cylinder body.
In second invention, even in blade component parts and the cylinder chamber in the total of the size in the size in the gap between the axial two side walls of cylinder body and the gap between the blade component parts, identical with the total in the size in the gap of the axial two side walls of cylinder body in blade under situation about blade being made of parts shown in the past and the cylinder chamber, also can reduce the amount that flows into the lubricant oil of low pressure chamber from the hyperbaric chamber.
Perhaps, in second invention, flow into from the hyperbaric chamber under the situation of the amount of the lubricant oil in the low pressure chamber and same degree in the past, can make the total of the size in the size in the gap between the lower wall surface on cylinder body axial of blade component parts and cylinder chamber and the gap between the blade component parts, big such as the total in the size in the gap of the axial two side walls of cylinder body in blade under the situation about blade being made of parts shown in the past and the cylinder chamber, can prevent reliably that the blade component parts from touching in the cylinder chamber the axial two side walls at cylinder body.
In addition, under the situation that blade is made of parts, can produce in the central part heat build-up of blades height direction burn sticking, but in second invention, owing to form blade by stacked a plurality of blade component parts, so the Clearance Flow lubricant oil between the blade component parts, it is sticking to be difficult to generate above-mentioned burning.
In the 3rd invention, can access the same effect of compressor with second invention.
In the 4th invention, since the integrally formed piston of roller and blade by cylinder body axially on stacked a plurality of piston component parts constitute, so can access the identical effect of compressor with first to the 3rd invention, and because integrally formed roller and blade, produce burning so can prevent both from sliding sticking.
Description of drawings
Fig. 1 is the summary construction diagram of the compressor of embodiments of the present invention.
Fig. 2 is the cylinder body of presentation graphs 1 and the planimetric map of structure of piston and their action.
Fig. 3 is the stereogram of the piston of Fig. 2.
Fig. 4 is the IV-IV line sectional drawing of Fig. 2, (a) expression mode of execution, (b) the existing mode of expression.
Fig. 5 is the V-V line sectional drawing of Fig. 2, (a) expression mode of execution, (b) the existing mode of expression.
Fig. 6 is illustrated in oil film reaction force and the big or small distribution thereof that takes place between the eccentric part of piston and main shaft, (a) is illustrated in gapless state between two piston component parts, (b) is illustrated in the state that has formed the gap between two piston component parts.
Fig. 7 is the diagram that is equivalent to Fig. 3 of variation 1.
Fig. 8 is the diagram that is equivalent to Fig. 2 of variation 2.
Fig. 9 is the diagram that is equivalent to Fig. 3 of variation 2.
Figure 10 is the diagram that is equivalent to Fig. 3 of variation 3.
Figure 11 is the diagram that is equivalent to Fig. 3 of variation 4.
Description of reference numerals
1 compressor
12 motors
13 compressing mechanisms
24 introducing ports
26 confined spaces
61 cylinder bodies
62 pistons
Cylinder chambers 71
The 71a side wall surface
The 71c low pressure chamber
The 71d hyperbaric chamber
81,82 piston component parts
81a, 82a roller formation portion
81b, 82b blade formation portion
81c, 82c outer circumferential face
91,92,93 piston component parts
101 rollers
102 blades
111,112 roller component parts
113,114 blade component parts
Embodiment
Below, with reference to the mode of execution of description of drawings compressor of the present invention.
Fig. 1 is the summary construction diagram of the compressor of present embodiment.Compressor 1 for example is the compressor that is used for aircondition such as air conditioner, and the refrigerant compression that is removed moisture that will import from accumulator 2 is discharged refrigerant after the compression from the discharge stream 25 that is configured in its upper end portion.As shown in Figure 1, compressor 1 is provided with housing 11, motor 12 and compressing mechanism 13.
Housing 11 is made of trunk 21, top 22 and bottom 23.Trunk 21 is the parts roughly cylindraceous that extend at above-below direction, its upper and lower end opening.In addition, in the side of trunk 21, form the connection mouth 24 of discharge tube 2a of the discharge refrigerant of two connection accumulators 2 along the vertical direction in the end, bottom right.Top 22 is the parts of opening that stop up the upper end of trunk 21.In addition, top 22 is provided with aforesaid discharge stream 25.Bottom 23 is the parts of opening that stop up the lower end of trunk 21.And, on housing 11, form the confined space 26 that surrounds by trunk 21, top 22 and bottom 23.
Motor 12 is configured in the confined space 26, has stator 31 and rotor 32.Stator 31 is fixed on the internal face of trunk 21.Rotor 32 is configured in the radially inner side of stator 31, in the upper end portion of the fixing main shaft 60 that extends along the vertical direction of its substantial middle portion.And in motor 12, rotor is rotated with main shaft 60 by the magnetic force that produces between rotor 32 at stator 31.In addition, the structure of stator 31 and rotor 32 is because identical with the structure of in the past motor, omits so describe in detail this its.
Compressing mechanism 13 is configured in the confined space 26, is positioned at the below of motor 12.Compressing mechanism 13 is the compressing mechanisms that are formed with the so-called rotary type of roller and blade, as shown in Figure 1, has cylinder body 61, piston 62, protecgulum 63, middle plate 64 and tail-hood 65.Fig. 2 is cylinder body 61 and the structure of piston 62 and the planimetric map of their action of presentation graphs 1.Fig. 3 is the stereogram of the piston 62 of Fig. 2.Fig. 4 is the IV-IV line sectional drawing of Fig. 2.Fig. 5 is the V-V line sectional drawing of Fig. 2.
As Fig. 1～shown in Figure 5, two cylinder bodies 61 are formed on the cylinder chamber 71 of overlooking circular that above-below direction connects cylinder body 61 along the above-below direction configuration of Fig. 1 in its substantial middle portion.And the upper and lower opening of the cylinder chamber 71 of the cylinder body 61 above being configured in is stopped up by protecgulum 63 and middle plate 64 respectively.On the other hand, the opening of upper and lower end of cylinder chamber 71 that is configured in the cylinder body 61 of below is stopped up by middle plate 64 and tail-hood 65 respectively.
In addition, on cylinder body 61, above Fig. 2 of cylinder chamber 71, be formed with and be communicated with cylinder chamber 71 and, the described later blade formation portion 81b that take in piston 62 upwardly extending, the blade accommodation chamber 75 of 82b at the upper and lower of Fig. 2.
In addition, be formed with introducing port 71b on the part on right side from Fig. 1 of the side wall surface 71a that is formed on cylinder chamber 71 to the importing stream 72 of the right-hand extension of Fig. 1 on cylinder body 61, the discharge tube 2a of the accumulator 2 that is connected with connection mouth 24 is connected and imports on the stream 72.Thus, import the refrigerant of compressor 1 via importing stream 72 from accumulator 2 from introducing port 71b inflow cylinder chamber 71 (low pressure chamber 71c described later in more detail).
Piston 62 is gone up at above-below direction (cylinder body 61 axially) by two piston component parts 81,82 and is stackedly constituted, and is configured in 71 inside, two cylinder chambers respectively.Piston component parts 81 constitutes the 81a of portion and blade by roller and constitutes the 81b of portion and constitute, and piston component parts 82 constitutes the 82a of portion and blade by roller and constitutes the 82b of portion and constitute, and piston component parts 81 and piston component parts 82 are of similar shape.
The roller formation 81a of portion, 82a overlook to constitute circularly, and laminated configuration is in the inside of cylinder chamber 71 mutually.The blade formation 81b of portion, 82b constitute with the roller formation 81a of portion, 82a one respectively, and extend the top in figure, upper end portion from Fig. 2 of outer circumferential face 81c, the 82c of the roller formation 81a of portion, 82a.
In addition, the blade formation 81b of portion, 82b are stacked mutually, the underpart of the Fig. 2 that connects with the roller formation 81a of portion, 82a is configured in the cylinder chamber 71 with the roller formation 81a of portion, 82a, and its upper end portion is configured in the blade accommodation chamber 75, similarly, can be bearing in slidably on the lining 73 that is disposed in the blade accommodation chamber 75.
In addition, roller formation 81a of portion and the roller formation 82a of portion stacked structure mutually are equivalent to roller of the present invention, and blade formation 81b of portion and the blade formation 82b of portion stacked structure mutually are equivalent to blade of the present invention.That is, in the present embodiment, roller and blade are integrally formed.Therefore, as described later, when piston 62 moved, roller and blade can not take place to slide and burn sticking.
And above-mentioned main shaft 60 connects the roller formation 81a of portion, 82a at above-below direction, is located at the space that eccentric part 60a in the way of main shaft 60, that its central shaft departs from from the central shaft of main shaft 60 embeds the inboard of the roller formation 81a of portion, 82a.Thus, in piston 62, when main shaft 60 rotation, the roller formation 81a of portion, 82a shown in Fig. 2 (a), Fig. 2 (d), the side wall surface 71a of its outer circumferential face 81c, 82c butt cylinder chamber 71 and moving to the clockwise direction of Fig. 2 along side wall surface 71a.
Piston 62 is so mobile, thereby cylinder chamber 71 is split into low pressure chamber 71c and hyperbaric chamber 71d by piston 62, and the volume-variation of low pressure chamber 71c and hyperbaric chamber 71d, shown in Fig. 2 (b), after outer circumferential face 81c, the 82c of the roller formation 81a of portion, 82a becomes the state of part of introducing port 71b downstream side adjacency of on the movement direction that is connected to the roller formation 81a of portion, 82a and side wall surface 71a cylinder chamber 71, to becoming between the state shown in Fig. 2 (d), the volume of hyperbaric chamber 71d reduces, and the refrigerant in the 71d of hyperbaric chamber is compressed.And when becoming the state of Fig. 2 (d), the above refrigerant of pressure that is compressed to the regulation in the 71d of hyperbaric chamber is discharged to confined space 26 from exhaust port 74.During this, on low pressure chamber 71c, import next compressed refrigerant from introducing port 71b.By carrying out above-mentioned action repeatedly, thereby be detained compressed refrigerant in confined space 26, the refrigerant that are trapped in the confined space 26 are discharged to the outside from discharging stream 25.
At this moment, for the last lower wall surface that prevents piston 62 contact cylinder chambers 71 (cylinder body 61 in the cylinder chamber 71 axially on two side walls), promptly, protecgulum 63, middle plate 64 and tail-hood 65 and obstruction piston 62 mobile, shown in Fig. 4,5, the height of piston 62, promptly the total Hp of the height of two piston component parts 81,82 (=(Hp/2)+(Hp/2)) is lower than the height H s of cylinder chamber 71.
Wherein, when the height of piston component parts 81,82 is spent low, then between the side of inner peripheral surface 81d, the 82d of the roller formation 81a of portion, 82a and eccentric part 60a, do not form the oil film of lubricant oil L, piston component parts 81,82 directly contact with eccentric part 60a and can produce burn sticking.But, in the present embodiment, the height H p/2 of piston component parts 81,82 such as Fig. 4 (a) are depicted as the height of the degree of the oil film that forms lubricant oil L between the side of inner peripheral surface 81d, the 82d of the roller formation 81a of portion, 82a and main shaft 60 (eccentric part 60a), thus, the roller formation 81a of portion, 82a can directly not contact with eccentric part 60a, can prevent both contact and produce burn sticking.
Like this, because the height H p of piston 62 is lower than the height H s of cylinder chamber 71, so via the interior side direction low pressure chamber 71c inflow lubricant oil L of the gap between the lower wall surface of the lower surface of gap between the upper wall surface of the upper surface of the roller formation 81a of portion and cylinder chamber 71 and the roller formation 82a of portion and cylinder chamber 71 from the roller formation 81a of portion, 82a.And, when for a long time, the temperature of the refrigerant in the low pressure chamber 71c is risen by this lubricant oil L from the quantitative change of the lubricant oil L of the interior side inflow low pressure chamber 71c of the roller formation 81a of portion, 82a, the performance of compressor 1 can reduce.
In addition, flow into lubricant oil L in the 71d of hyperbaric chamber via the gap between the lower wall surface of the lower surface of gap between the upper wall surface of the upper surface of the blade formation 81b of portion and cylinder chamber 71 and the blade formation 82b of portion and cylinder chamber 71.In the 71d of hyperbaric chamber, owing to carry out the compression of refrigerant as mentioned above, so the temperature of the refrigerant in the 71d of hyperbaric chamber uprises, flow into from hyperbaric chamber 71d low pressure chamber 71c lubricant oil L quantitative change for a long time, by this lubricant oil L the temperature of the refrigerant in the low pressure chamber 71c is risen, the performance of compressor 1 is reduced.
But, in the present embodiment, piston 62 constitutes in that above-below direction is mutually stacked by two piston component parts 81,82, so not only between the upper wall surface of the upper surface of piston component parts 81 and cylinder chamber 71 and between the lower wall surface of the lower surface of piston component parts 82 and cylinder chamber 71, and between piston component parts 81 and piston component parts 82, also flow into lubricant oil L and form oil film, thereby can form the gap.
Therefore, as Fig. 4 (b), shown in Fig. 5 (b), when with piston 62 ' under the situation that situation about being made of parts shown in is in the past compared, when establish piston 62 ' height and two piston component parts 81, the total of 82 height is identical, during for Hp, piston 62 in this case ' upper surface and the big or small B1 in the gap between the upper wall surface of cylinder chamber 71 and piston 62 ' lower surface and the total B1+B2 of the big or small B2 in the gap between the lower wall surface of cylinder chamber 71, with under the situation of present embodiment, the big or small A1 in the gap between the upper wall surface of the upper surface of piston component parts 81 and cylinder chamber 71, the big or small A2 in the gap between the lower wall surface of the lower surface of piston component parts 82 and cylinder chamber 71, and the total A1+A2+A3 of the big or small A3 in the gap between piston component parts 81 and the piston component parts 82 is identical.
In addition, big or small A1, the A2 in the above-mentioned gap under the situation of present embodiment, A3 approximate equality (1/3rd degree of the total in these gaps promptly).On the other hand, also approximate equality (size of 1/2nd degree of the total in these gaps promptly) of big or small B1, the B2 in the above-mentioned gap under the situation in the past.Therefore, under the situation of present embodiment, since can between piston component parts 81 and piston component parts 82, form the gap, big or small A1, the A2 in each gap in the present embodiment, A3 are littler than big or small B1, the B in each gap shown in Fig. 4 (b), Fig. 5 (b).
At this, flow through the flow Q of liquid in the interlobate gap of two Zhang Pings as can be known for (numerical expression 1) from hydromechanical viewpoint:
Q = - h 3 12 μ · dp dx
At this, h is that the size in gap, viscosity, the dp/dx that μ is lubricant oil L are pressure gradient.And, according to this formula as can be known, because the flow Q of liquid in the gap between flat blade of flowing through is directly proportional with the cube of the big or small h in gap, so that the gap has is a plurality of, under the identical situation of the total of the size in gap, the total of the flow Q of big slight its liquid of person in many and each gap of the quantity in gap is few.
Therefore, shown in present embodiment, piston 62 is by under the situation about constituting at stacked two the piston component parts 81,82 of above-below direction, can reduce the gap of lower wall surface of the lower surface of gap, piston component parts 82 between the upper wall surface of the upper surface of piston component parts 81 and cylinder chamber 71 and cylinder chamber 71 and big or small A1, A2, the A3 in the gap between piston component parts 81 and the piston component parts 82, can reduce via these gaps from the inside of the roller formation 81a of portion, 82a and the amount that flows into the lubricant oil L of low pressure chamber 71c from hyperbaric chamber 71d.Thus, can prevent from the temperature of the refrigerant in the low pressure chamber 71c to be risen, can prevent that the performance of compressor 1 from reducing by the lubricant oil L of high temperature.
In other words, when the amount of the above-mentioned lubricant oil L that flows into low pressure chamber 71c also with identical in the past situation under, can make the total A1+A2+A3 of size in above-mentioned gap bigger than the total B1+B2 of the size in the past gap, promptly, the height that can make piston component parts 81 and the total of the height of piston component parts 82 than piston 62 ' height low, hinder the mobile of piston 62 so can prevent the last lower wall surface of piston contact cylinder chambers 71 62 reliably.
At this, under the situation of present embodiment, because big or small B1, the B2 in big or small A1, the A2 in above-mentioned gap ratio gap in the past are little, so the lower wall surface of the lower surface of the upper wall surface of the upper surface of piston component parts 81 and cylinder chamber 71 and piston component parts 82 and cylinder chamber 71 is respectively near configuration, piston component parts 81,82 is the last lower wall surface of contact cylinder chamber 71 easily.
But, not not equal according to the linear expansion amount of deformation of cylinder body 61 and piston 62, when piston component parts 81,82 with the last lower wall surface of cylinder chamber 71 near the time, by piston component parts 81,82 with the last lower wall surface of cylinder chamber 71 between and the L shaped oil film that becomes of piston component parts 81 and the lubricant oil between the piston component parts 82 pressed off, thereby piston component parts 81 moves (promptly to close mutually direction with piston component parts 82, the big or small A3 in gap diminishes), piston component parts 81 and piston component parts 82 are if the gap that moves between the two disappears, then only can form between the upper wall surface of the upper surface of piston component parts 81 and cylinder chamber 71 and between the lower wall surface of the lower surface of piston component parts 82 and cylinder chamber 71 with in the past piston 62 ' the identical gap of situation, so compared with the past, piston 62 can not move to the last lower wall surface of cylinder chamber 71 easily.
In addition, at this, even piston component parts 81 is stacked at above-below direction with piston component parts 82, different with above-mentioned structure, if between piston component parts 81 and piston component parts 82, can not form gap (if A3=0 of Fig. 4 (a), Fig. 5 (a)), then the distance A 1 of the last lower wall surface of piston component parts 81,82 and cylinder chamber 71, A2 respectively with shown in Fig. 4 (b), Fig. 5 (b) apart from B1, B same degree, promptly, distance A 1, A2 and not little apart from B1, B2.
But, in the present embodiment, shown in Fig. 6 (a), under state very close to each other between piston component parts 81 and the piston component parts 82, when main shaft 60 rotation and piston component parts 81,82 when moving, the then power effect that is laminated between inner peripheral surface 81d, the 82d of the outer circumferential face of eccentric part 60a and the roller formation 81a of portion, 82a is defeated out lubricant oil L between them by this, so the power (oil film reaction force) that effect pushes back from lubricant oil L on inner peripheral surface 81d, 82d.At this, Fig. 6 (a) is the diagram that is illustrated in the distribution of oil film reaction force under the state very close to each other between two piston component parts 81,82, that produce and size thereof between the eccentric part 60a of piston 62 and main shaft 60.
Shown in Fig. 6 (a), the size of this oil film reaction force, because at the central part of the above-below direction of the piston component parts 81,82 that constitutes one, promptly, the part maximum between piston component parts 81 and the piston component parts 82, so by the oil film reaction force, between piston component parts 81 and piston component parts 82, flow into lubricant oil L, can form the gap by between.Therefore, in the action of compressor 1, can between piston component parts 81 and piston component parts 82, form the gap reliably.
In addition, the size of the above-mentioned oil film reaction force after can forming the gap between piston component parts 81 and the piston component parts 82, shown in Fig. 6 (b), the central part at the above-below direction of piston component parts 81,82 is then big more, and upper and lower end parts is then more little.At this, Fig. 6 (b) is the diagram that is illustrated in the distribution of oil film reaction force under the state that can form the gap between two piston component parts 81,82, that produce and size thereof between the eccentric part 60a of piston 62 and main shaft 60.
In addition, shown in Fig. 4 (b), Fig. 5 (b), under the situation of piston 62 ' constitute by parts, piston 62 ' the substantial middle portion heat build-up of above-below direction of blade part (with the blade formation 81b of portion shown in Fig. 5 (b), the part that 82b is corresponding), can produce burn sticking.
But, in the present embodiment, piston 62 is by constituting at stacked two the piston component parts 81,82 of above-below direction, current lubrication oil L between blade formation 81b of portion and the blade formation 82b of portion, so can heat build-up between blade formation 81b of portion and the blade formation 82b of portion, it is sticking to prevent to produce above-mentioned burning.
In addition, in compressor 1, can use CO as refrigerant 2And, use CO as refrigerant 2Situation under, the pressure difference between low pressure chamber and the hyperbaric chamber is big especially, flows into lubricant oil L from hyperbaric chamber 71d to low pressure chamber 71c easily.But, under such situation, as mentioned above, the amount that can reduce between the upper wall surface via the upper surface of piston component parts 81 and cylinder chamber 71, between the lower wall surface of the lower surface of piston component parts 82 and cylinder the chamber 71 and gap between piston component parts 81 and the piston component parts 82 flows into the lubricant oil L of low pressure chamber 71c from inside and the hyperbaric chamber 71d of the roller formation 81a of portion, 82a.
In addition, using as refrigerant in the compressor 1 of CO2, when being used for the situation etc. of hot watering supply device, owing to uprise from the temperature of the refrigerant of compressor 1 ejection, so when from the high hyperbaric chamber 71d of temperature when the low low pressure chamber 71c of temperature flows into lubricant oil L, the temperature of the refrigerant in the low pressure chamber rises, and the compression efficiency of the refrigerant of compressor 1 can reduce.
But, in the present embodiment, as mentioned above, because can reduce between the upper wall surface via the upper surface of piston component parts 81 and cylinder chamber 71, between the lower wall surface of the lower surface of piston component parts 82 and cylinder the chamber 71 and gap between piston component parts 81 and the piston component parts 82 is from the inside of the roller formation 81a of portion, 82a and from the amount of the lubricant oil L of hyperbaric chamber 71d inflow low pressure chamber 71c, so can reduce the reduction of the compression efficiency of such refrigerant.
In addition, in compressor 1, can also use by molecular formula C 3H mF nHave single refrigerant that the refrigerant of 1 two key constitutes or the mixed cooling medium that comprises this refrigerant in (wherein, m=1～5, n=1～5, and m+n=6) expression and the structure of molecule as refrigerant.
Particularly, can use 2,3,3,3-tetrafluoro-1-propylene (is called " HFO-1234yf ", with chemical formula CF 3-CF=CH 2The expression), 1,2,3,3-five fluoro-1-propylene (are called " HFO-1225ye ", with chemical formula CF 3-CF=CHF represents), 1,3,3,3-tetrafluoro-1-propylene (is called " HFO-1234ze ", with chemical formula CHF 2-CF=CHF represents), 1,2,3,3-tetrafluoro-1-propylene (is called " HFO-1234ye ", with chemical formula CHF 2-CF=CHF represents), 3,3,3-three fluoro-1-propylene (are called " HFO-1234zf ", with chemical formula CF 3-CF=CH 2The expression), 1,2,2-three fluoro-1-propylene are (with chemical formula CH 3-CF=CF 2Expression), 2-fluoro-1-propylene is (with chemical formula CH 3-CF=CH 2Expression) etc.
In addition, can also use and in above-mentioned refrigerant, add HFC-32 (Difluoroethane), HFC-125 (pentafluoroethane), HFC-134 (1,1,2, the 2-HFC-134a), HFC-134a (1,1,1, the 2-HFC-134a), HFC-143a (1,1, the 1-HFC-143a), HFC-152a (1, the 1-Difluoroethane), HFC-161, HFC-227ea, HFC-236ea, HFC-236fa, HFC-365mfc, methane, ethane, propane, propylene, butane, isobutane, pentane, the 2-methyl butane, cyclopentane, dimethyl ether, two (trifluoromethyl) thioether, carbon dioxide, at least a in the helium and the mixed cooling medium that obtains.
And, known above-mentioned refrigerant (C 3H mF n) its theoretic achievement coefficient (COP) is than higher, the achievement coefficient (COP) of the device of use compressor 1 improves.In addition, such refrigerant does not comprise chlorine atom and bromine atoms etc., to the influence little ((GWP) is little for the global warming coefficient) of the destruction of ozonosphere.
But,,, need to increase the volume of cylinder chamber 71 so compare with the situation of using other refrigerant because the refrigerating capacity of above-mentioned its per unit volume of refrigerant is lower.At this moment,, consider to improve the height of cylinder chamber 71, but under the situation that the height of cylinder chamber 71 improves, the height that is configured in the piston in the cylinder chamber 71 uprises also in order to increase the volume of cylinder chamber 71.Therefore, as (for example the piston 62 shown in Fig. 4 (b), Fig. 5 (b) ' shown in) shown in the past when piston is made of parts, in the central part heat build-up especially easily of the blade-section of piston, be easy to generate burn sticking.
With respect to this, in the present embodiment, piston 62 constitutes by piston component parts 81 and piston component parts 82 are stacked, thus can heat build-up between blade formation 81b of portion and the blade formation 82b of portion, and it is sticking to prevent to produce above-mentioned burning reliably.
In addition, above-mentioned refrigerant is because when becoming high temperature, refrigerant decomposes easily, so preferably use being difficult to become under the situation of high temperature, but in the present embodiment, as mentioned above, the piston 62 that uprises easily with temperature ' the substantial middle portion piston component parts 81 corresponding, piston 62 of above-below direction and the part between the piston component parts 82 by lubricant oil L cooling, so can prevent that refrigerant is decomposed.
As mentioned above, in the compressor 1 of present embodiment, because piston 62 is by two stacked on above-below direction piston component parts 81,82 constitute, so big or small A1 in the gap between the upper wall surface of the upper surface of piston component parts 18 and cylinder chamber 71, the big or small A2 in the gap between the lower wall surface of the lower surface of piston component parts 82 and cylinder chamber 71, and the total A1+A2+A3 of the big or small A3 in the gap between piston component parts 81 and the piston component parts 82, even with in the past shown in the piston 62 ' identical that constitutes by parts with the total of the big or small B1+B2 in the gap of the last lower wall surface of cylinder chamber, because the big or small A1 in each gap, A2, the size of A3 is than the big or small B1 in each gap under the situation in the past, B2 is little, so can reduce from the roller formation 81a of portion, the inboard of 82a and hyperbaric chamber 71d flow into the amount of the lubricant oil L of low pressure chamber 71c.Thus, make the temperature of the refrigerant in the low pressure chamber 71c be difficult to rise, can prevent that the performance of compressor 1 from reducing by lubricant oil L.
In addition, under the situation of the amount of the above-mentioned lubricant oil L that flows into low pressure chamber 71c and same degree in the past, the total of the height of piston component parts 81,82 can be reduced, the last lower wall surface of piston component parts contact cylinder chambers 71 81,82 can be prevented reliably.
In addition, owing to the oil of current lubrication between blade formation 81b of portion and the blade formation 82b of portion L, produce burning so can prevent heat build-up between blade formation 81b of portion and the blade formation 82b of portion sticking.
In addition, piston component parts 81,82 is respectively the roller formation 81a of portion and the blade formation 81b of portion and roller formation 82a of portion and the integrally formed parts of the blade formation 82b of portion, produce so can prevent the roller formation 81a of portion and the blade formation 81b of portion and the roller formation 82a of portion and the blade formation 82b of portion from sliding burn sticking.
More than, embodiments of the present invention have been described with reference to the accompanying drawings, but concrete structure is not limited to these mode of executions, can change in the scope of the main idea that does not break away from invention.
In the above-described embodiment, piston 62 is by constituting at stacked two the piston component parts 81,82 of above-below direction, still being not limited thereto.In a variation, as shown in Figure 7, piston 90 by above-below direction stacked, highly be that three piston component parts 91,92,93 of Hp/3 degree constitute (variation).
In this case, owing to forming oil film flowing into lubricant oil L (with reference to Fig. 4) between piston component parts 91 and the piston component parts 92 and between piston component parts 92 and the piston component parts 93, thereby can form the gap, so the size in gap between the lower wall surface of the lower surface of the gap between the upper wall surface of the upper surface of piston component parts 91 and cylinder chamber 71 (with reference to Fig. 4), piston component parts 93 and cylinder chamber 71 and the gap between the piston component parts 91～93 is littler than (particularly, above-mentioned B1, B2) in the past.Thus, with above-mentioned mode of execution similarly, can reduce the amount that flows into the lubricant oil L of low pressure chamber 71c (with reference to Fig. 4) from inside and the hyperbaric chamber 71d (with reference to Fig. 4) of the roller formation 91a of portion, 92a, 93a via these gaps.
In addition, owing to the oil of current lubrication between the blade formation 91b of portion, 92b, 93b L, produce burning so can prevent the part heat build-up between the blade formation 91b of portion, 92b, 93b sticking.
Wherein, under the situation of variation 1, the height H p/3 of each piston component parts 91～93 also becomes the height of the degree of the oil film that can form lubricant oil L between inner peripheral surface 91d, 92d, 93d and the eccentric part 60a of the roller formation 91a of portion, 92a, 93a.
In addition, piston also can be formed with the upper piston component parts by stacked four of above-below direction.Wherein, follow the number that increases the piston component parts, the height of each piston component parts diminishes, and forms number more than the height of the minimum that forms oil film between the inner peripheral surface of roller formation portion and the eccentric part 60a so the number of piston component parts need be a height with each piston component parts.
In addition, in the above-described embodiment, in piston component parts 81,82, roller formation 81a of portion and the blade formation 81b of portion and the roller formation 82a of portion and the blade formation 82b of portion are integrally formed, and roller and blade-shaped become one thus, but are not limited thereto.In another variation, as Fig. 8, shown in Figure 9, overlook and see that roughly the roller 101 of ring is configured in the cylinder chamber 71, and blade 102 is striden cylinder chamber 71 and 105 configurations of blade accommodation chamber.In addition, the upper end portion at Fig. 8 of blade accommodation chamber 105 disposes the spring 103 that blade 102 is pushed to the below of Fig. 8 towards roller 101.In addition, roller 101 is made of two roller component parts 111,112 stacked on above-below direction, and blade 102 constitutes (variation 2) by two blade component parts 113,114 stacked on above-below direction.
In this wise, even under the situation that roller 101 and blade 102 form respectively, also with above-mentioned mode of execution similarly, gap between the upper wall surface of the lower surface of the upper surface of roller component parts 111 and blade component parts 113 and cylinder chamber 71, gap between the lower wall surface of the lower surface of the lower surface of roller component parts 112 and roller component parts 112 and cylinder chamber 71, gap between roller component parts 111 and the roller component parts 112, and the gap smaller between blade component parts 113 and the blade component parts 114, from roller component parts 111, the amount that 112 inboard and hyperbaric chamber 71d flow into the lubricant oil L of low pressure chamber 71c is minimized.
In addition since between blade component parts 113 and blade component parts 114 current lubrication oil L, so with above-mentioned mode of execution in the same manner, can prevent the part heat build-up between blade component parts 113 and blade component parts 114 and produce burn sticking.
In addition, as refrigerant, as use the C that comprises that illustrates in the above-mentioned mode of execution 3H mF nThe situation of refrigerant under, when becoming high temperature, refrigerant decomposes easily, so preferably use being difficult to become under the situation of high temperature.With respect to this, in the compressor that the roller of variation 2 and blade form respectively, by the slip generation heat of roller and blade, this part of compressor becomes high temperature easily.
But, in variation 2, as mentioned above, roller 101 is by constituting at stacked two the roller component parts 111,112 of above-below direction, blade 102 is by constituting at stacked two the blade component parts 113,114 of above-below direction, so at current lubrication oil L between roller component parts 111 and the roller component parts 112 and between blade component parts 113 and the blade component parts 114, by this part of lubricant oil L cooling compressor.Therefore, can prevent to cause refrigerant to decompose by the temperature rising of compressor.
In addition, in above-mentioned variation 2, roller 101 is made of two roller component parts 111,112, and blade 102 is made of two blade component parts 113,114, but is not limited thereto.
In another variation, as shown in figure 10, roller 101 and variation 2 similarly be made of two roller component parts 111,112, but blade 102 also can constitute (variation 3) by parts.In this case, also with above-mentioned mode of execution similarly, can reduce from the amount of the lubricant oil L of the interior side inflow low pressure chamber 71c of roller component parts 111,112.
In addition, in another variation, as shown in figure 11, blade 102 and variation 2 similarly, constitute by two blade component parts 113,114, but roller 101 also can constitute (variation 4) by parts.In this case, also with above-mentioned mode of execution similarly, can reduce the amount that flows into the lubricant oil L of low pressure chamber 71c from hyperbaric chamber 71d, and can prevent the part heat build-up between blade component parts 113 and blade component parts 114 and produce to burn and glue.
In addition, roller 101 is made of a plurality of roller component parts, and under blade 102 situation about being made of a plurality of blade component parts, and the number of the number of roller component parts and blade component parts also can be different mutually.In this case, can access the effect same with above-mentioned variation 2.
In addition, in the above-described embodiment, main shaft 60 extends (the axial of cylinder body 61 is above-below direction) at above-below direction, piston component parts 81,82 is stacked at above-below direction, but be not limited thereto, under the situation that main shaft extends in the horizontal direction (cylinder body axially under the situation of substantially horizontal), a plurality of piston component parts can be gone up stacked at the bearing of trend of main shaft (cylinder body axially).
In addition, above mode of execution is essentially preferred example, does not represent restriction the present invention, its suitable thing or its purposes scope.
Utilizability on the industry
Utilize the present invention to reduce to flow into the amount of the lubricating oil of low-pressure chamber, can prevent from causing the temperature rise of the refrigerant in the low-pressure chamber and making the hydraulic performance decline of compressor by lubricating oil.

Claims (4)

1. a compressor (1) is characterized in that:
Have: cylinder body (61), it is configured in the confined space (26), and is provided with cylinder chamber (71) in inside;
The roller of ring-type (81a, 82a, 91a, 92a, 93a, 101), it is configured in the inside of described cylinder chamber (71), the side wall surface (71a) of its outer circumferential face (81c, 82c) butt described cylinder chamber (71) and moving along this side wall surface (71a), described cylinder chamber (71) is divided into the compression of carrying out refrigerant and compressed refrigerant is discharged to the hyperbaric chamber (71d) of described confined space (26) and imports the low pressure chamber (71c) of refrigerant from the outside, and make the volume-variation of described hyperbaric chamber (71d) and described low pressure chamber (71c); And
Blade (81b, 82b, 91b, 92b, 93b, 102), it is configured in the inside of described cylinder chamber (71), (81a, 82a, 91a, 92a, 93a, 101) is divided into described hyperbaric chamber (71d) and described low pressure chamber (71c) with described cylinder chamber (71) with described roller
Described roller (81a, 82a, 91a, 92a, 93a, 101) by described cylinder body axially on stacked a plurality of roller component parts (81a, 82a, 91a, 92a, 93a, 111,112) constitute.
2. compressor as claimed in claim 1 (1), it is characterized in that, described blade (81b, 82b, 91b, 92b, 93b, 102) by described cylinder body axially on stacked a plurality of blade component parts (81b, 82b, 91b, 92b, 93b, 113,114) constitute.
3. a compressor (1) is characterized in that:
Have: cylinder body (61), it is configured in the confined space (26), and is provided with cylinder chamber (71) in inside;
The roller of ring-type (81a, 82a, 91a, 92a, 93a, 101), it is configured in the inside of described cylinder chamber (71), the side wall surface (71a) of its outer circumferential face (81c, 82c) butt described cylinder chamber (71) and moving along this side wall surface (71a), described cylinder chamber (71) is divided into the compression of carrying out refrigerant and compressed refrigerant is discharged to the hyperbaric chamber (71d) of described confined space (26) and imports the low pressure chamber (71c) of refrigerant from the outside, and make the volume-variation of described hyperbaric chamber (71d) and described low pressure chamber (71c); And
Blade (81b, 82b, 91b, 92b, 93b, 102), it is configured in the inside of described cylinder chamber (71), (81a, 82a, 91a, 92a, 93a, 101) is divided into described hyperbaric chamber (71d) and described low pressure chamber (71c) with described cylinder chamber (71) with described roller
Described blade (81b, 82b, 91b, 92b, 93b, 102) by described cylinder body axially on stacked a plurality of blade component parts (81b, 82b, 91b, 92b, 93b, 113,114) constitute.
4. a compressor (1) is characterized in that:
Have: cylinder body, it is configured in the confined space (26), and is provided with cylinder chamber (71) in inside; And
Piston (62), it is configured in the inside of described cylinder chamber (71),
Described piston (62) has:
The roller of ring-type (81a, 82a, 91a, 92a, 93a), the side wall surface (71a) of its outer circumferential face (81c, 82c) butt described cylinder chamber (71) and moving along this side wall surface (71a), described cylinder chamber (71) is divided into the compression of carrying out refrigerant and compressed refrigerant is discharged to the hyperbaric chamber (71d) of described confined space (26) and imports the low pressure chamber (71c) of refrigerant from the outside, and make the volume-variation of described hyperbaric chamber (71d) and described low pressure chamber (71c); And
Blade (81b, 82b, 91b, 92b, 93b), itself and described roller (81a, 82a, 91a, 92a, 93a) are integrally formed, (81a, 82a, 91a, 92a, 93a) is divided into described hyperbaric chamber (71d) and described low pressure chamber (71c) with described cylinder chamber (71) with described roller
And, described piston (62) by described cylinder body axially on stacked a plurality of piston component parts (81,82,91,92,93) constitute.
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