CN101925743B

CN101925743B - Compressor

Info

Publication number: CN101925743B
Application number: CN200980103011.XA
Authority: CN
Inventors: 小川步; 足立诚; 西本康伸
Original assignee: Daikin Industries Ltd
Current assignee: Daikin Industries Ltd
Priority date: 2008-01-23
Filing date: 2009-01-23
Publication date: 2014-05-07
Anticipated expiration: 2029-01-23
Also published as: WO2009093701A1; JP2009197793A; CN101925743A; JP4488104B2; JP5018829B2; JP2009197806A

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 recording, in the internal configurations of cylinder chamber that is formed at the inside of cylinder body, be formed with the piston of roller and blade in patent documentation 1, by piston, cylinder chamber be divided into suction chamber (low pressure chamber) and spray chamber (hyperbaric chamber).And, in the time of side wall surface by roller butt cylinder chamber, along this side wall surface, move, thus the volume-variation of ejection chamber and compress the indoor refrigerant of ejection.

Patent documentation 1: Japanese Patent Laid-Open 2004-124948 communique

At this, in the compressor of recording in patent documentation 1, in order to prevent that piston from hindering it to move with the contacting of upper lower wall surface of cylinder chamber, piston (roller and blade) is lower than cylinder chamber height.In addition, due to, roller is lower than cylinder chamber height, so via the gap of the upper lower wall surface of roller and cylinder chamber, the lubricant oil of the inner side of the roller of flowing through flows into low pressure chamber.But, when the quantitative change of the lubricant oil of the interior side inflow low pressure chamber from roller is many, by this lubricant oil, cause the temperature of the refrigerant in low pressure chamber to rise, the performance of compressor reduces.

In addition, because blade is lower than cylinder chamber height, so via the gap of the upper lower wall surface of blade and cylinder chamber, lubricant oil flows into low pressure chamber from hyperbaric chamber.At this, owing to carrying out the compression of refrigerant in hyperbaric chamber, so the temperature in hyperbaric chamber uprises, thus, the temperature of the lubricant oil in hyperbaric chamber also uprises.Therefore, when flowing into the quantitative change of lubricant oil of low pressure chamber from hyperbaric chamber when many, the temperature of the refrigerant in low pressure chamber rises, and 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 object 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 the first invention is characterized in that having: cylinder body, and it is configured in confined space, and is provided with cylinder chamber in inside; The roller of ring-type, it is configured in the inside of described cylinder chamber, the side wall surface of cylinder chamber described in its outer circumferential face butt and moving along this side wall surface, described cylinder chamber is divided into compression the hyperbaric chamber that compressed refrigerant is discharged to described confined space of carrying out refrigerant and the low pressure chamber that imports refrigerant from outside, and makes the volume-variation of described hyperbaric chamber and described low pressure chamber; And blade, it is configured in the inside of described cylinder chamber, together 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 form.

In this compressor, due to by cylinder body axially on stacked a plurality of roller component parts form roller, so form the oil film of lubricant oil between roller component parts in the driving of compressor, between roller component parts, can form gap, in roller component parts and cylinder chamber about the size in the gap between the axial two side walls of cylinder body and the size in the gap between roller component parts, the gap in the roller in situation about being formed by parts such as roller shown in the past and cylinder chamber between the axial two side walls of cylinder body slight greatly.On the other hand, from the amount of the liquid in the known inflow of hydromechanical viewpoint gap in the situation that the big or small total in gap is identical, when the quantity in gap is more, a gap large slight fewer.

Therefore, in roller component parts and cylinder chamber in the size in the gap between the axial two side walls of cylinder body and the big or small total in the gap between roller component parts, even with as shown in the past, by parts, formed in roller in the situation of roller and cylinder chamber in the big or small total in the gap of the axial two side walls of cylinder body identically, also can reduce the amount of the lubricant oil that flows into low pressure chamber.

Or, in the situation of the amount degree as in the past of the lubricant oil in inflow low pressure chamber, can make in roller component parts and cylinder chamber in the size in the gap between the axial two side walls of cylinder body and the big or small total in the gap between roller component parts, such as the size in the gap of the axial two side walls of cylinder body in the roller in situation about roller being consisted of parts shown in the past and cylinder chamber is large, can prevent reliably that roller component parts from touching in cylinder chamber the axial two side walls at cylinder body.

In addition, in this compressor, can form the amount in gap between roller component parts, make in roller component parts and cylinder chamber to shorten about the distance of the axial two side walls of cylinder body, not but not equal according to the line dilatancy amount of cylinder body and piston, in cylinder chamber in the axial two side walls of cylinder body during near roller component parts, oil film is pressed off, thereby the gap smaller between roller component parts, so compare with situation in the past, roller can easily not contact in cylinder chamber the wall in the axial both sides of cylinder body yet.

The compressor of the second invention, on the basis of the compressor of the first invention, is characterized in that, by described cylinder body axially on stacked a plurality of blade component parts form.

In this compressor, because a plurality of blade component parts by stacked form blade, so can and blade component parts between form the oil film of lubricant oil, can between blade component parts, form gap, the gap in the blade in situation about being formed by parts such as blade shown in the past about the size in the gap between the axial two side walls of cylinder body and the size in the gap between blade component parts in blade component parts and cylinder chamber and cylinder chamber between the axial two side walls of cylinder body slight greatly.

Therefore, even in blade component parts and cylinder chamber in the size in the gap between the axial two side walls of cylinder body and the big or small total in the gap between blade component parts, big or small total in the gap of the axial two side walls of cylinder body in blade in situation about as shown in the past, blade being consisted of parts and cylinder chamber is identical, also can reduce the amount that flows into the lubricant oil of low pressure chamber from hyperbaric chamber.

Or, the situation of the amount degree as in the past of the lubricant oil in hyperbaric chamber flows into low pressure chamber, can make the size in the gap between blade component parts and the upper lower wall surface of cylinder chamber and the big or small total in the gap between blade component parts, such as the big or small total in the gap of the axial two side walls of cylinder body in the blade in situation about blade being consisted of parts shown in the past and cylinder chamber is large, can prevent reliably that blade component parts from touching in cylinder chamber the axial two side walls at cylinder body.

In addition, in the situation that blade consists of parts, can produce in the central part heat build-up of the short transverse of blade burn sticky, but in this compressor, owing to forming blade by stacked a plurality of blade component parts, so the Clearance Flow lubricant oil between blade component parts, is difficult to generate above-mentioned burning sticky.

In addition, in this compressor, can form the amount in gap between blade component parts, make in blade component parts and cylinder chamber to shorten in the distance of the axial two side walls of cylinder body, not but not equal according to the line dilatancy amount of cylinder body and piston, in cylinder chamber in the axial two side walls of cylinder body during near blade component parts, oil film is pressed off, thereby the gap smaller between blade component parts, so compare with situation in the past, blade can easily not contact in cylinder chamber the wall in the axial both sides of cylinder body yet.

The compressor of the 3rd invention is characterized in that having: cylinder body, and it is configured in confined space, and is provided with cylinder chamber in inside; The roller of ring-type, it is configured in the inside of described cylinder chamber, the side wall surface of cylinder chamber described in its outer circumferential face butt and moving along this side wall surface, described cylinder chamber is divided into compression the hyperbaric chamber that compressed refrigerant is discharged to described confined space of carrying out refrigerant and the low pressure chamber that imports refrigerant from outside, and makes the volume-variation of described hyperbaric chamber and described low pressure chamber; And blade, it is configured in the inside of described cylinder chamber, together 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 form.

In this compressor, can access the effect same with the compressor of the second invention.

The compressor of the 4th invention, is characterized in that having: cylinder body, and it is configured in confined space, and is provided with 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 cylinder chamber described in its outer circumferential face butt and moving along this side wall surface, described cylinder chamber is divided into compression the hyperbaric chamber that compressed refrigerant is discharged to described confined space of carrying out refrigerant and the low pressure chamber that imports refrigerant from outside, and makes the volume-variation of described hyperbaric chamber and described low pressure chamber; And, blade, itself and described roller are integrally formed, and together 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 form.

In this compressor, due to the piston that is integrally formed roller and blade by cylinder body axially on stacked a plurality of piston component parts form, so can access the effect identical with the compressor of the first to the 3rd invention, and owing to being integrally formed roller and blade, so can prevent both from sliding, producing to burn and glue.

(invention effect)

As mentioned above, according to the present invention, can access following effect.

In the first invention, even roller component parts and the size in cylinder chamber in the situation that the gap between the axial two side walls of cylinder body and the big or small total in the gap between roller component parts with as shown in the past, by parts, formed in the roller of roller and cylinder chamber in the big or small total in the gap of the axial two side walls of cylinder body identically, also can reduce the amount of the lubricant oil that flows into low pressure chamber.

Or, in the first invention, in the situation of the amount degree as in the past of the lubricant oil in inflow low pressure chamber, can make in roller component parts and cylinder chamber in the size in the gap between the axial two side walls of cylinder body and the big or small total in the gap between roller component parts, such as the size in the gap of the axial two side walls of cylinder body in the roller in situation about roller being consisted of parts shown in the past and cylinder chamber is large, can prevent reliably that roller component parts from touching in cylinder chamber the axial two side walls about cylinder body.

In the second invention, even in blade component parts and cylinder chamber in the size in the gap between the axial two side walls of cylinder body and the big or small total in the gap between blade component parts, big or small total in the gap of the axial two side walls of cylinder body in blade in situation about as shown in the past, blade being consisted of parts and cylinder chamber is identical, also can reduce the amount that flows into the lubricant oil of low pressure chamber from hyperbaric chamber.

Or, in the second invention, the situation of the amount degree as in the past of the lubricant oil in hyperbaric chamber flows into low pressure chamber, can make the size in the gap between the axial upper lower wall surface of cylinder body and the big or small total in the gap between blade component parts of blade component parts and cylinder chamber, such as the big or small total in the gap of the axial two side walls of cylinder body in the blade in situation about blade being consisted of parts shown in the past and cylinder chamber is large, can prevent reliably that blade component parts from touching in cylinder chamber the axial two side walls at cylinder body.

In addition, in the situation that blade consists of parts, can produce in the central part heat build-up of the short transverse of blade burn sticky, but in the second invention, owing to forming blade by stacked a plurality of blade component parts, so the Clearance Flow lubricant oil between blade component parts, is difficult to generate above-mentioned burning sticky.

In the 3rd invention, can access the effect same with the compressor of the second invention.

In the 4th invention, the piston being integrally formed due to roller and blade by cylinder body axially on stacked a plurality of piston component parts form, so can access the effect identical with the compressor of the first to the 3rd invention, and owing to being integrally formed roller and blade, so can prevent both from sliding, producing to burn and glue.

Accompanying drawing explanation

Fig. 1 is the summary construction diagram of the compressor of embodiments of the present invention.

Fig. 2 means the planimetric map of the cylinder body of Fig. 1 and the 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) represents (b) to represent existing mode by mode of execution.

Fig. 5 is the V-V line sectional drawing of Fig. 2, (a) represents (b) to represent existing mode by mode of execution.

Fig. 6 means oil film reaction force and the big or small distribution thereof occurring between piston and the eccentric part of main shaft, (a) be illustrated in gapless state between two piston component parts, (b) be illustrated in the state that has formed 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

71 cylinder chambers

71a side wall surface

71c low pressure chamber

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 accompanying drawings of the mode of execution of compressor of the present invention.

Fig. 1 is the summary construction diagram of the compressor of present embodiment.Compressor 1 is such as being compressor for airconditions such as air conditioners, the refrigerant compression that is removed moisture that will import from accumulator 2, the refrigerant of discharging compression from being configured in the discharge stream 25 of its upper end portion.As shown in Figure 1, compressor 1 is provided with housing 11, motor 12 and compressing mechanism 13.

Housing 11 consists of trunk 21, top 22 and bottom 23.Trunk 21 is the roughly parts cylindraceous that extend at above-below direction, its upper and lower end opening.In addition, in the side of trunk 21, in end, bottom right, form along the vertical direction the connection mouth 24 of discharge tube 2a of the discharge refrigerant of two connection accumulators 2.Top 22 is the parts of opening that stop up the upper end of trunk 21.In addition, on top 22, be 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 being surrounded by trunk 21, top 22 and bottom 23.

Motor 12 is configured in 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 extending along the vertical direction of its substantial middle portion.And in motor 12, rotor is rotation together with main shaft 60 by the magnetic force producing between rotor 32 at stator 31.In addition, the structure of stator 31 and rotor 32 is because the structure of the motor with is in the past identical, so describe in detail and omit this its.

Compressing mechanism 13 is configured in 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 means the planimetric map of the cylinder body 61 of Fig. 1 and the structure of piston 62 and their action.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 shown in Fig. 1～Fig. 5, two cylinder bodies 61, along the above-below direction configuration of Fig. 1, are formed in its substantial middle portion the cylinder chamber 71 of overlooking circular that above-below direction connects cylinder body 61.And, be configured in top cylinder body 61 cylinder chamber 71 upper and lower opening respectively by protecgulum 63 and in plate 64 stop up.On the other hand, be configured in below cylinder body 61 cylinder chamber 71 upper and lower end opening respectively by plate 64 and tail-hood 65 stop up.

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 at the upper and lower of Fig. 2, the blade accommodation chamber 75 of 82b.

In addition, be formed with introducing port 71b in the part on right side from be formed on Fig. 1 of side wall surface 71a of 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 being connected with connection mouth 24 is connected to and imports on stream 72.Thus, the refrigerant that imports compressor 1 from accumulator 2 is via importing stream 72 from introducing port 71b inflow cylinder chamber 71 (low pressure chamber 71c described later in more detail).

Piston 62 stackedly consists of above-below direction (cylinder body 61 axially) is upper two

piston component parts

81,82, is configured in respectively 71 inside, two cylinder chambers.Piston component parts 81 forms the 81a of portion and blade by roller and forms the 81b of portion and form, and piston component parts 82 forms the 82a of portion and blade by roller and forms the 82b of portion and form, and piston component parts 81 and piston component parts 82 are of similar shape.

The roller formation 81a of portion, 82a overlook to form circularly, and laminated configuration is in the inside of cylinder chamber 71 mutually.The blade formation 81b of portion, 82b form with the roller formation 81a of portion, 82a one respectively, and extend to top in figure the 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 mutually stacked, the underpart of the Fig. 2 connecting with the roller formation 81a of portion, 82a is configured in cylinder chamber 71 together with the roller formation 81a of portion, 82a, and its upper end portion is configured in blade accommodation chamber 75, similarly, can be bearing in slidably on the lining 73 being disposed in blade accommodation chamber 75.

In addition, the roller formation 81a of portion and the roller formation 82a of portion mutually stacked structure are equivalent to roller of the present invention, and the blade formation 81b of portion and the blade formation 82b of portion mutually stacked structure 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 moves, roller and blade can not occur to slide and burn sticky.

And above-mentioned main shaft 60 connects the roller formation 81a of portion, 82a at above-below direction, be 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 inner side of the roller formation 81a of portion, 82a.Thus, in piston 62, when main shaft 60 rotation, the roller formation 81a of portion, 82a as 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 clockwise direction along from side wall surface 71a to Fig. 2 moves.

Piston 62 is so mobile, thereby cylinder chamber 71 is separated 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, as shown in Fig. 2 (b), outer circumferential face 81c, the 82c of the roller formation 81a of portion, 82a becomes after 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 while becoming the state of Fig. 2 (d), the refrigerant being compressed to more than the pressure of 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, from introducing port 71b, import next compressed refrigerant.By repeatedly carrying out above-mentioned action, thereby in confined space 26, be detained compressed refrigerant, the refrigerant being trapped in confined space 26 is discharged to outside from discharging stream 25.

At this moment, for prevent piston 62 contact cylinder chambers 71 upper lower wall surface (cylinder body 61 in cylinder chamber 71 axially on two side walls),, protecgulum 63, middle plate 64 and tail-hood 65 and the movement of obstruction piston 62, as shown in Figure 4,5, the height of piston 62, 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 too low, between inner peripheral surface 81d, the 82d of the roller formation 81a of portion, 82a and the side of 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 sticky.But, in the present embodiment, the height H p/2 of

piston component parts

81,82 is depicted as the height of the degree of the oil film that forms lubricant oil L between inner peripheral surface 81d, the 82d of the roller formation 81a of portion, 82a and the side of main shaft 60 (eccentric part 60a) as Fig. 4 (a), thus, the roller formation 81a of portion, 82a can directly not contact with eccentric part 60a, can prevent both contact and produce burn sticky.

Like this, because the height H p of piston 62 is lower than the height H s of cylinder chamber 71, so flow into lubricant oil L via the gap between the gap between the upper surface of the roller formation 81a of portion and the upper wall surface of cylinder chamber 71 and the lower surface of the roller formation 82a of portion and the lower wall surface of cylinder chamber 71 from the interior side direction low pressure chamber 71c of the roller formation 81a of portion, 82a.And, when the quantitative change of the lubricant oil L of the interior side inflow low pressure chamber 71c from the roller formation 81a of portion, 82a is many, by this lubricant oil L, make the temperature of the refrigerant in low pressure chamber 71c increase, the performance of compressor 1 can reduce.

In addition, via the lubricant oil L in inflow hyperbaric chamber, the gap 71d between the gap between the upper surface of the blade formation 81b of portion and the upper wall surface of cylinder chamber 71 and the lower surface of the blade formation 82b of portion and the lower wall surface of cylinder chamber 71.In the 71d of hyperbaric chamber, owing to carrying out as mentioned above the compression of refrigerant, so the temperature of the refrigerant in the 71d of hyperbaric chamber uprises, from hyperbaric chamber 71d, flow into the quantitative change of lubricant oil L of low pressure chamber 71c when many, by this lubricant oil L, make the temperature of the refrigerant in low pressure chamber 71c increase, can make the performance of compressor 1 reduce.

But, in the present embodiment, piston 62 consists of above-below direction is mutually stacked two

piston component parts

81,82, so not only between the upper surface of piston component parts 81 and the upper wall surface of cylinder chamber 71 and between the lower surface of piston component parts 82 and the lower wall surface of 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 gap.

Therefore, as Fig. 4 (b), shown in Fig. 5 (b), in the situation of comparing with the situation of piston 62 ' formed by parts as shown in the past, 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 in 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 piston component parts 82 is identical.

In addition, big or small A1, the A2 in the above-mentioned gap in the situation of present embodiment, A3 approximate equality (, 1/3rd degree of the total in these gaps).On the other hand, also approximate equality (, the size of 1/2nd degree of the total in these gaps) of big or small B1, the B2 in the above-mentioned gap in situation in the past.Therefore, the in the situation that of present embodiment, owing to forming gap between piston component parts 81 and piston component parts 82, big or small A1, the A2 in each gap in present embodiment, A3 are less than big or small B1, the B in each gap shown in Fig. 4 (b), Fig. 5 (b).

At this, from the flow Q of the liquid in the known gap between two flat blades of flowing through of hydromechanical viewpoint, be (numerical expression 1):

Q = - \frac{h^{3}}{12 μ} \cdot \frac{dp}{dx}

At this, the size that h is gap, μ are that viscosity, the dp/dx of lubricant oil L is pressure gradient.And, known according to this formula, because the flow Q of the liquid in the gap between flat blade of flowing through is directly proportional to the cube of the big or small h in gap, so that gap has is a plurality of, in the identical situation of the big or small total in gap, the total of the flow Q of large slight its liquid of person in many and each gap of the quantity in gap is few.

Therefore, as shown in the embodiment, piston 62 by the situation that stacked two the

piston component parts

81,82 of above-below direction form, can reduce big or small A1, A2, the A3 in gap and the gap between piston component parts 81 and piston component parts 82 of gap, the lower surface of piston component parts 82 and the lower wall surface of cylinder chamber 71 between the upper surface of piston component parts 81 and the upper wall surface of cylinder chamber 71, the amount that can reduce via these gaps from the inside of the roller formation 81a of portion, 82a and flow into the lubricant oil L of low pressure chamber 71c from hyperbaric chamber 71d.Thus, can prevent from making the temperature of the refrigerant in low pressure chamber 71c increase by the lubricant oil L of high temperature, can prevent that the performance of compressor 1 from reducing.

In other words, when the amount of above-mentioned lubricant oil L that flows into low pressure chamber 71c is also in situation as in the past, the big or small total A1+A2+A3 that can make above-mentioned gap is larger than the big or small total B1+B2 in gap in the past,, can make the height of piston component parts 81 and the total of the height of piston component parts 82 than piston 62 ' height low, so can prevent reliably the upper lower wall surface of piston 62 contact cylinder chambers 71, hinder the movement of piston 62.

At this, the in the situation that of present embodiment, because big or small A1, the A2 in above-mentioned gap are less than big or small B1, the B2 in gap in the past, 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 approaches respectively configuration,

piston component parts

81,82 is the upper lower wall surface of contact cylinder chamber 71 easily.

But, not not equal according to the line dilatancy amount of cylinder body 61 and piston 62, when

piston component parts

81, 82 when approach with the upper lower wall surface of cylinder chamber 71, by

piston component parts

81, 82 with the upper lower wall surface of cylinder chamber 71 between and the L shaped oil film becoming of piston component parts 81 and lubricant oil between piston component parts 82 pressed off, thereby (piston component parts 81 moves to mutually close direction with piston component parts 82, the big or small A3 in gap diminishes), if the gap that piston component parts 81 and piston component parts 82 move between the two disappears, only between the upper surface of piston component parts 81 and the upper wall surface of cylinder chamber 71 and between the lower surface of piston component parts 82 and the lower wall surface of cylinder chamber 71, can form with piston 62 in the past ' the identical gap of situation, so compared with the past, piston 62 can easily not move to the upper lower wall surface of cylinder chamber 71.

In addition, at this, even if piston component parts 81 is stacked at above-below direction with piston component parts 82, different from above-mentioned structure, if can not form gap (if A3=0 of Fig. 4 (a), Fig. 5 (a)) between piston component parts 81 and piston component parts 82, the distance A 1 of the upper lower wall surface of

piston component parts

81,82 and cylinder chamber 71, A2 respectively with distance B1, the B same degree shown in Fig. 4 (b), Fig. 5 (b),, distance A 1, A2 and not little apart from B1, B2.

But, in the present embodiment, as shown in Fig. 6 (a), under state very close to each other between piston component parts 81 and piston component parts 82, when main shaft 60 rotation and

piston component parts

81,82 while moving, the power effect being laminated between the outer circumferential face of eccentric part 60a and inner peripheral surface 81d, the 82d of the roller formation 81a of portion, 82a, by this, defeat out the lubricant oil L between them, 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) means the diagram of the distribution of oil film reaction force under state very close to each other between two

piston component parts

81,82, that produce between piston 62 and the eccentric part 60a of main shaft 60 and size thereof.

As shown in Fig. 6 (a), the size of this oil film reaction force, part due to the central part of the above-below direction of the

piston component parts

81,82 being integrally formed,, between piston component parts 81 and piston component parts 82 is maximum, so by oil film reaction force, between piston component parts 81 and piston component parts 82, flow into lubricant oil L, can form gap by between.Therefore, in the action of compressor 1, can between piston component parts 81 and piston component parts 82, form gap reliably.

In addition, between piston component parts 81 and piston component parts 82, can form the size of the above-mentioned oil film reaction force behind gap, as shown in Fig. 6 (b), larger at the central part of the above-below direction of

piston component parts

81,82, upper and lower end parts is less.At this, Fig. 6 (b) means the diagram of the distribution of oil film reaction force under the state that can form gap between two

piston component parts

In addition, as shown in Fig. 4 (b), Fig. 5 (b), in the situation of piston 62 ' formed 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 sticky.

But, in the present embodiment, piston 62 is by forming at stacked two the

piston component parts

81,82 of above-below direction, current lubrication oil L between the blade formation 81b of portion and the blade formation 82b of portion, so can heat build-up between the blade formation 81b of portion and the blade formation 82b of portion, can prevent that above-mentioned burning is sticky.

In addition, in compressor 1, as refrigerant, can use CO ₂.And, as refrigerant, use CO ₂situation under, the pressure difference between low pressure chamber and hyperbaric chamber is large especially, easily from hyperbaric chamber 71d to low pressure chamber 71c, flows into lubricant oil L.But, in such situation, as mentioned above, can reduce the amount that 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 via the gap between the upper surface of piston component parts 81 and the upper wall surface of cylinder chamber 71, between the lower surface of piston component parts 82 and the lower wall surface of cylinder chamber 71 and between piston component parts 81 and piston component parts 82.

In addition, as refrigerant, using in the compressor 1 of CO2, during for the situation of hot watering supply device etc., because the temperature of the refrigerant from compressor 1 ejection uprises, so when flowing into lubricant oil L from the high hyperbaric chamber 71d of temperature to the low low pressure chamber 71c of temperature, the temperature of the refrigerant in low pressure chamber rises, and the compression efficiency of the refrigerant of compressor 1 can reduce.

But, in the present embodiment, as mentioned above, owing to can reducing via the gap between the upper surface of piston component parts 81 and the upper wall surface of cylinder chamber 71, between the lower surface of piston component parts 82 and the lower wall surface of cylinder chamber 71 and between piston component parts 81 and piston component parts 82 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, 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 _n(wherein, m=1～5, n=1～5, and m+n=6) represent and structure of molecule in there is the single refrigerant that the refrigerant of 1 two key forms or the mixed cooling medium that comprises this refrigerant as refrigerant.

Particularly, can use 2,3,3,3-tetrafluoro-1-propene (to be called " HFO-1234yf ", with chemical formula CF ₃-CF=CH ₂represent), 1,2,3, the fluoro-1-propylene of 3-five (is called " HFO-1225ye ", with chemical formula CF ₃-CF=CHF represents), 1,3,3,3-tetrafluoro-1-propene (is called " HFO-1234ze ", with chemical formula CHF ₂-CF=CHF represents), 1,2,3,3-tetrafluoro-1-propene (is called " HFO-1234ye ", with chemical formula CHF ₂-CF=CHF represents), 3,3, the fluoro-1-propylene of 3-tri-(is called " HFO-1234zf ", with chemical formula CF ₃-CF=CH ₂represent), 1,2, the fluoro-1-propylene of 2-tri-is (with chemical formula CH ₃-CF=CF ₂expression), the fluoro-1-propylene of 2-is (with chemical formula CH ₃-CF=CH ₂represent) etc.

In addition, can also use and in above-mentioned refrigerant, add HFC-32 (Difluoroethane), HFC-125 (pentafluoroethane), HFC-134 (1, 1, 2, 2-HFC-134a), HFC-134a (1, 1, 1, 2-HFC-134a), HFC-143a (1, 1, 1-HFC-143a), HFC-152a (1, 1-Difluoroethane), HFC-161, HFC-227ea, HFC-236ea, HFC-236fa, HFC-365mfc, methane, ethane, propane, propylene, butane, isobutane, pentane, 2-methyl butane, cyclopentane, dimethyl ether, two (trifluoromethyl) thioether, carbon dioxide, at least one in helium and the mixed cooling medium that obtains.

And, known above-mentioned refrigerant (C ₃h _mf _n) its theoretic achievement coefficient (COP) is higher, uses the achievement coefficient (COP) of the device of compressor 1 to improve.In addition, such refrigerant does not comprise chlorine atom and bromine atoms etc., on the impact of the destruction of ozonosphere little ((GWP) is little for global warming coefficient).

But, because the refrigerating capacity of above-mentioned its per unit volume of refrigerant is lower, so compare with using the situation of other refrigerant, need to increase the volume of cylinder chamber 71.At this moment, in order to increase the volume of cylinder chamber 71, consider to improve the height of cylinder chamber 71, but in the situation that the height of cylinder chamber 71 improves, the height that is configured in the piston in cylinder chamber 71 also uprises.Therefore, for example, when as shown in the past, (piston 62 shown in Fig. 4 (b), Fig. 5 (b) ' shown in) piston consists of parts, in the especially easily heat build-up of central part of the blade-section of piston, easily produce burn sticky.

With respect to this, in the present embodiment, piston 62 is by piston component parts 81 and piston component parts 82 is stacked forms, thus can heat build-up between the blade formation 81b of portion and the blade formation 82b of portion, can prevent reliably that above-mentioned burning is sticky.

In addition, above-mentioned refrigerant is due to when becoming high temperature, refrigerant easily decomposes, so preferably use being difficult to become under the situation of high temperature, but in the present embodiment, as mentioned above, the piston 62 easily uprising with temperature ' substantial middle portion piston component parts 81 corresponding, piston 62 and the part between piston component parts 82 of above-below direction cooling by lubricant oil L, so can prevent that refrigerant is decomposed.

As mentioned above, in the compressor 1 of present embodiment, because piston 62 is by two piston component parts 81 stacked on above-below direction, 82 form, 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 piston component parts 82, even with in the past shown in the piston 62 ' identical with the total of the big or small B1+B2 in the gap of the upper lower wall surface of cylinder chamber that formed by parts, big or small A1 due to each gap, A2, the size of A3 is than the big or small B1 in each gap in situation in the past, B2 is little, so can reduce from the roller formation 81a of portion, the inner side of 82a and hyperbaric chamber 71d flow into the amount of the lubricant oil L of low pressure chamber 71c.Thus, by lubricant oil L, make the temperature of the refrigerant in low pressure chamber 71c be difficult to rise, can prevent that the performance of compressor 1 from reducing.

In addition, in the situation that flow into the amount degree as in the past of the above-mentioned lubricant oil L of low pressure chamber 71c, the total of the height of

piston component parts

81,82 can be reduced, the upper lower wall surface of

piston component parts

81,82 contact cylinder chambers 71 can be prevented reliably.

In addition, due to the oil of current lubrication between the blade formation 81b of portion and the blade formation 82b of portion L, so can prevent heat build-up between the blade formation 81b of portion and the blade formation 82b of portion, produce to burn and glue.

In addition,

piston component parts

81,82 is respectively the parts that 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 are integrally formed, 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, produce burn sticky.

Above, 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 in the scope of main idea that does not depart from invention, change.

In the above-described embodiment, piston 62 is by forming at stacked two the

piston component parts

81,82 of above-below direction, but is not limited to this.In a variation, as shown in Figure 7, piston 90 by above-below direction stacked, be highly that three

piston component parts

91,92,93 of Hp/3 degree form (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 piston component parts 92 and between piston component parts 92 and piston component parts 93, thereby can form gap, so the size in the gap between gap, the lower surface of piston component parts 93 and the lower wall surface of cylinder chamber 71 between the upper surface of piston component parts 91 and the upper wall surface of cylinder chamber 71 (with reference to Fig. 4) and the gap between piston component parts 91～93 is less than (above-mentioned B1, B2 particularly) 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, due to the oil of current lubrication between the blade formation 91b of portion, 92b, 93b L, so can prevent the part heat build-up between the blade formation 91b of portion, 92b, 93b, produce to burn and glue.

Wherein, the in the situation that 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 upper piston component parts by stacked four of above-below direction.Wherein, follow the number that increases piston component parts, the height of each piston component parts diminishes, so the number of piston component parts need to be that the height of each piston component parts is formed to the number more than the height of minimum that forms oil film between the inner peripheral surface of roller formation portion and eccentric part 60a.

In addition, in the above-described embodiment, in

piston component parts

81,82, 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 are integrally formed, and roller and blade-shaped become one thus, but are not limited to this.In another variation, as shown in Figure 8, Figure 9, overlook and see that roughly the roller 101 of ring is configured in cylinder chamber 71, and blade 102 is across

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 pressed to the below of Fig. 8 towards roller 101.In addition, roller 101 consists of two roller component parts 111,112 stacked on above-below direction, and blade 102 forms (variation 2) by two blade component parts 113,114 stacked on above-below direction.

In this wise, even in 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 roller component parts 112, and the gap smaller between blade component parts 113 and blade component parts 114, from roller component parts 111, the amount that 112 inner side and hyperbaric chamber 71d flow into the lubricant oil L of low pressure chamber 71c is minimized.

In addition, due to current lubrication between blade component parts 113 and blade component parts 114 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 sticky.

In addition, as refrigerant, the C that comprises illustrating in above-mentioned mode of execution as used ₃h _mf _nthe situation of refrigerant under, when becoming high temperature, refrigerant easily decomposes, 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 easily becomes high temperature.

But, in variation 2, as mentioned above, roller 101 is by forming at stacked two the roller component parts 111,112 of above-below direction, blade 102 is by forming 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 roller component parts 112 and between blade component parts 113 and blade component parts 114, by this part of lubricant oil L cooling compressor.Therefore, can prevent from causing refrigerant to decompose by the temperature rising of compressor.

In addition, in above-mentioned variation 2, roller 101 consists of two roller component parts 111,112, and blade 102 consists of two blade component parts 113,114, but is not limited to this.

In another variation, as shown in figure 10, roller 101 and variation 2 similarly, consist of, but blade 102 also can form (variation 3) by parts two roller component parts 111,112.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, by two blade component parts 113,114, formed, but roller 101 also can form (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 consists of a plurality of roller component parts, and in blade 102 situation about consisting of a plurality of blade component parts, the number of roller component parts also can be mutually different from the number of blade component parts.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 to this, in the situation that main shaft extends in the horizontal direction (in the axially situation for substantially horizontal of cylinder body), a plurality of piston component parts can be upper 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 applicable thing or its purposes scope.

Utilizability in industry

Utilize the present invention to reduce to flow into the amount of the lubricant oil of low pressure chamber, can prevent from causing the temperature of the refrigerant in low pressure chamber to rise and making the hydraulic performance decline of compressor by lubricant oil.

Claims

1. a compressor (1), is characterized in that:

Have: cylinder body (61), it is configured in confined space (26), and in inside, is provided with cylinder chamber (71);

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 cylinder chamber (71) described in its outer circumferential face (81c, 82c) butt and mobile along this side wall surface (71a), described cylinder chamber (71) is divided into and carries out the compression of refrigerant and compressed refrigerant be discharged to the hyperbaric chamber (71d) of described confined space (26) and from outside, import the low pressure chamber (71c) of refrigerant, and make the volume-variation of described hyperbaric chamber (71d) and described low pressure chamber (71c);

Blade (81b, 82b, 91b, 92b, 93b, 102), it is configured in the inside of described cylinder chamber (71), together with described roller (81a, 82a, 91a, 92a, 93a, 101), described cylinder chamber (71) is divided into described hyperbaric chamber (71d) and described low pressure chamber (71c); With

A spring, it is pressed described blade (81b, 82b, 91b, 92b, 93b, 102) towards described roller (81a, 82a, 91a, 92a, 93a, 101),

Described blade (81b, 82b, 91b, 92b, 93b, 102) by described cylinder body axially on stacked and formed by a plurality of blade component parts (81b, 82b, 91b, 92b, 93b, 113,114) to described roller (81a, 82a, 91a, 92a, 93a, 101) by described spring.