CN101802404A - Closed type compressor and freezing apparatus using the same - Google Patents

Closed type compressor and freezing apparatus using the same Download PDF

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Publication number
CN101802404A
CN101802404A CN200980100463A CN200980100463A CN101802404A CN 101802404 A CN101802404 A CN 101802404A CN 200980100463 A CN200980100463 A CN 200980100463A CN 200980100463 A CN200980100463 A CN 200980100463A CN 101802404 A CN101802404 A CN 101802404A
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angle
piston
pressing chamber
type compressor
axle
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CN200980100463A
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CN101802404B (en
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明石浩业
森田一郎
取枡宏树
小林正则
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Panasonic Holdings Corp
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Matsushita Electric Industrial Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/02—Lubrication
    • F04B39/0223—Lubrication characterised by the compressor type
    • F04B39/023—Hermetic compressors
    • F04B39/0238—Hermetic compressors with oil distribution channels
    • F04B39/0246—Hermetic compressors with oil distribution channels in the rotating shaft
    • F04B39/0253—Hermetic compressors with oil distribution channels in the rotating shaft using centrifugal force for transporting the oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
    • F04B39/122—Cylinder block

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)

Abstract

轴承部(120)和压缩室(115)被布置成使得示出轴承部(120)的轴心的第一中心线(141)与示出压缩室(115)的轴心的第二中心线(142)可以彼此相交，在第一中心线(141)与第二中心线(142)之间形成的角度a1以及预定角度b1可以满足公式1的关系，并且通过与基于轴承部(120)和主轴部(111)的间隙的、轴(110)相对于轴承部(120)的倾斜角度的绝对值c1相关联来设定角度b1，从而可以防止活塞与压缩室(115)之间的撬动。

Figure 200980100463

The bearing section (120) and the compression chamber (115) are arranged such that a first center line (141) showing the axis of the bearing section (120) and a second center line (142) showing the axis of the compression chamber (115) can intersect each other. Angle a1 formed between the first center line (141) and the second center line (142) and a predetermined angle b1 can satisfy the relationship of Formula 1. Angle b1 is set by relating it to the absolute value c1 of the tilt angle of the shaft (110) relative to the bearing section (120) based on the gap between the bearing section (120) and the main shaft section (111), thereby preventing prying between the piston and the compression chamber (115).

Figure 200980100463

Description

Hermetic type compressor and use the refrigeration equipment of this hermetic type compressor
Technical field
The present invention relates to a kind of hermetic type compressor that in the refrigeration cycle of refrigerator refrigerator etc., uses, and the freezing and refrigerating equipment that uses this hermetic type compressor.
Background technique
Recently, require to be used for freezing and hermetic type compressor refrigerating equipment of refrigerator refrigerator and other and raise the efficiency reducing power consumption, and reduce noise and improve reliability.In the middle of the hermetic type compressor of this class routine, have some by change fuel supply method to the joint between connecting rod and the piston improved efficient and stability (referring to, for example, PTL1).
Followingly describe with reference to the example of accompanying drawing to this routine hermetic type compressor.Figure 20 is the longitudinal section of disclosed conventional hermetic type compressor in the patent documentation 1.Figure 21 is the amplification sectional view of the major component of Figure 20.Figure 22 is the sectional view of the major component of Figure 20.
As shown in Figure 20 and Figure 21, seal container 1 holds the motor-driven components 4 with stator 2 and rotor 3, and the compressing member 5 that is driven by motor-driven components 4.Lubricant oil 6 is stored in the bottom of seal container 1.Axle 10 has main shaft part 11, and forms eccentric axial portion 12 with main shaft part 11 mass motions prejudicially at an end of main shaft part 11.Main shaft part 11 is fixed in the axle center of rotor 3.
Cylinder body 14 has pressing chamber 15 and the bearing portion 20 that is arranged to interfix in the approximate circle tubular of special position.In pressing chamber 15, but to-and-fro motion ground inserts piston 23.
Piston 23 has and is engaged the wrist pin 25 parallel with eccentric axial portion 12.Bearing portion 20 forms cantilever bearings by the end of eccentric axial portion 12 sides in the main shaft part 11 of back shaft 10.
Connecting rod 26 is made of big stomidium portion 28, small end hole portion 29 and bar portion 30.Big stomidium portion 28 fits closely on the eccentric axial portion 12, and small end hole portion 29 is connected in wrist pin 25.Therefore, eccentric axial portion 12 and piston 23 link together.The inwall of small end hole portion 29 has the sphere portion 31 of convex-shaped, when near the axial centre of small end hole portion 29, contacting with each other with convenient wrist pin 25 and small end hole portion 29, small end hole portion 29 axially on two ends form the gap.
Fuel feeding path 35 is arranged on the inside of axle 10, and spills the end that oil pipe 36 is coupled to eccentric axial portion 12 sides of fuel feeding path 35.The opposition side end of the eccentric axial portion 12 of main shaft part 11, promptly stretch out underpart 40, makes lubricant oil 6 can immerse in the fuel feeding path 35 to prescribed depth.
In having the hermetic type compressor of this configuration, its operational instruction is as follows.Rotor 3 running shafts 10 of motor-driven components 4.Therefore, rotatablely moving of eccentric axial portion 12 is passed to piston 23 by connecting rod 26.Thus, piston 23 to-and-fro motion in pressing chamber 15.By the to-and-fro motion of piston 23, refrigerant gas is drawn into the pressing chamber 15 from the cooling system (not shown), and is compressed and is discharged in the cooling system once more.
The underpart of fuel feeding path 35 is designed to play by the rotation of axle 10 effect of pump.By this pumping action, the lubricant oil 6 of seal container 1 bottom is upwards aspirated by fuel feeding path 35.Arrive the lubricant oil 6 on fuel feeding path 35 tops, shown in arrow X, upwards flatly spray by the whole week of centrifugal force seal container 1 from the top of spilling oil pipe 36.The part of the lubricant oil 6 that sprays is supplied with lube pistons pin 25, piston 23 etc.
Because the sphere portion 31 that the inwall of small end hole portion 29 has convex-shaped if therefore produce the power that prizes connecting rod 26 up and down, then because the contact segment of sphere portion 31 departs from, can prevent that the part of wrist pin 25 and small end hole portion 29 from prizing.In addition, a large amount of lubricant oil 6 can be provided to the slide part of wrist pin 25 and small end hole portion 29, obtain high reliability and high efficiency thus.
Yet, in this conventional hermetic type compressor, be not enough to prevent the prizing between the inwall 15a of piston 23 and pressing chamber 15 of generation when the compression load of compression refrigerant gas works.
With reference to the sectional view of the major component among Figure 22, the generation that prizes between the inwall 15a of piston 23 and pressing chamber 15 is described.
As shown in Figure 22, in the compression stroke of refrigerant gas, act on the eccentric axial portion 12 by connecting rod 26 in the compression load F that produces on the piston 23.Owing to have the gap between main shaft part 11 and bearing portion 20, therefore when compression load F acted on the eccentric axial portion 12, axle 10 was positioned at the axle center 20A of bearing portion 20, and main shaft part 11 tilts to angle c at utmost in bearing portion 20.Therefore, eccentric axial portion 12 is (that is, based on the axle center 12A of the eccentric axial portion 12 in the axle center that is parallel to main shaft part 11) angle of inclination dc also from the axle center of main shaft part 11, and the relative angle in the axle center between pressing chamber 15 and the bearing portion 20 also changes.Therefore, piston 23 as shown in Figure 22, its center tilts.
In this conventional hermetic type compressor, by on the inwall of small end hole portion 29, forming convex shape, can suppress the inclination of piston 23, but can not prevent the generation that prizes between the inwall 15a of piston 23 and pressing chamber 15.
Because prizing of producing between the inwall 15a of piston 23 and pressing chamber 15, therefore in the part of piston 23 with the slip surface of the inwall 15a slip of pressing chamber 15, that is, by the part at the edge of the upper-end surface shown in the P, surface pressure increases partly in the drawings.Therefore, even in small end hole portion 29, have in the hermetic type compressor of routine of convex-shaped inwall, still there are the premature wear such as piston 23, the problem that wear extent increases and slippage loss increases.Reference listing
Patent documentation
PTL 1: patent documentation 1: Japanese kokai publication hei 09-317644 communique
Summary of the invention
Exploitation of the present invention is in order to overcome the above problems, and its objective is that therefore providing a kind of can prevent prizing, suppressing wearing for piston, reduce slippage loss and further improving the hermetic type compressor of reliability and efficient between piston and the pressing chamber.
The invention provides a kind of hermetic type compressor of the compressing member that in seal container, accommodates motor-driven components and drive by this motor-driven components, wherein compressing member comprises: axle, it has the main shaft part by motor-driven components rotation and driving, and is formed on an end of main shaft part and the eccentric axial portion that main shaft part is integrally moved; Bearing portion, its main shaft part by back shaft forms cantilever bearings; Cylinder body, it is arranged to be fixed on the special position in the bearing portion, and forms columnar pressing chamber; Be inserted into can be in pressing chamber pistons reciprocating; And the connecting rod that is used to connect eccentric axial portion and piston, and, the line that bearing portion and pressing chamber are arranged such that the axle center of bearing portion or are parallel to the axle center of bearing portion can intersect each other with the axle center of pressing chamber, by the axle center of bearing portion or be parallel to the line in axle center of bearing portion and angle a1 (rad) and predetermined angle b1 (rad) that the axle center of pressing chamber forms satisfy formula (1), and by with based on the gap between bearing portion and the main shaft part, axle is associated set angle b1 with respect to the absolute value c1 (rad) at the angle of inclination of bearing portion.
a1＝π/2+b1(rad) (1)
The present invention also provides a kind of hermetic type compressor of the compressing member that accommodates motor-driven components and driven by this motor-driven components in seal container, wherein compressing member comprises: axle, it has the main shaft part by motor-driven components rotation and driving, and is formed on an end of main shaft part and the eccentric axial portion that main shaft part is integrally moved; Bearing portion, its main shaft part by back shaft forms cantilever bearings; Cylinder body, it is arranged to be fixed on the special position in the bearing portion, and forms columnar pressing chamber; Be inserted into can be in pressing chamber to-and-fro motion and have the piston of pin-and-hole; Be inserted and secured on the wrist pin in the pin-and-hole; And be used to connect eccentric axial portion and piston, and at one end have big stomidium portion and have the connecting rod of small end hole portion at the other end, the angle a2 (rad) and the predetermined angle b2 (rad) that are formed by the axle center of the axle center of piston and pin-and-hole satisfy formula (2), and by with based on the gap between bearing portion and the main shaft part, axle is associated set angle b2 with respect to the absolute value c2 (rad) at the angle of inclination of bearing portion.
a2＝π/2+b2(rad) (2)
The present invention also provides a kind of hermetic type compressor of the compressing member that accommodates motor-driven components and driven by this motor-driven components in seal container, wherein compressing member comprises: axle, it has the main shaft part by motor-driven components rotation and driving, and is formed on an end of main shaft part and the eccentric axial portion that main shaft part is integrally moved; Bearing portion, its main shaft part by back shaft forms cantilever bearings; Cylinder body, it is arranged to be fixed on the special position in the bearing portion, and forms columnar pressing chamber; Be inserted into can be in pressing chamber to-and-fro motion and have the piston of pin-and-hole; Be inserted and secured on the wrist pin in the pin-and-hole; And be used to connect eccentric axial portion and wrist pin, and at one end have big stomidium portion and have the connecting rod of small end hole portion at the other end, the angle a3 (rad) that forms by the axle center of the axle center of big stomidium portion and small end hole portion be constituted as based on the gap between bearing portion and the main shaft part, spool with respect to the absolute value c3 (rad) at the angle of inclination of bearing portion more than 0.5 times to below 3.3 times.
In this configuration, can prevent prizing between piston and the pressing chamber.Therefore, piston wear reduces and reliability improves, and slippage loss reduces and obtained high efficiency.
Description of drawings
Fig. 1 is the longitudinal section of the hermetic type compressor in the preferred embodiments of the present invention 1.
Fig. 2 is the amplification sectional view of the major component when compression load does not work in same preferred embodiment.
Fig. 3 is the amplification sectional view of the major component when compression load works in same preferred embodiment.
Fig. 4 is the sectional view of major component that the relative position of bearing portion in the same preferred embodiment and pressing chamber is shown.
Fig. 5 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.
Fig. 6 is the sectional view of upper surface that the relative position of bearing portion in the same preferred embodiment and pressing chamber is shown.
Fig. 7 is near the sectional view of the major component of the pressing chamber in the preferred embodiments of the present invention 2.
Fig. 8 is near the sectional view of the major component of the pressing chamber in the same preferred embodiment.
Fig. 9 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.
Figure 10 is the longitudinal section of the hermetic type compressor in the preferred embodiments of the present invention 3.
Figure 11 is the amplification sectional view of the major component when compression load does not work in same preferred embodiment.
Figure 12 is the amplification sectional view of the major component when compression load works in same preferred embodiment.
Figure 13 is the sectional view of major component that the relative position of piston in the same preferred embodiment and pin-and-hole is shown.
Figure 14 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.
Figure 15 is the amplification sectional view of the major component when compression load does not work in the preferred embodiments of the present invention 4.
Figure 16 is the amplification sectional view of the major component when compression load works in same preferred embodiment.
Figure 17 is the sectional view of major component that the relative position of the big stomidium portion of the connecting rod in the same preferred embodiment and small end hole portion is shown.
Figure 18 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.
Figure 19 is the schematic configuration diagram of the refrigerator refrigerator in the preferred embodiments of the present invention 5.
Figure 20 is the longitudinal section of conventional hermetic type compressor.
Figure 21 is the amplification sectional view of the major component among Figure 20.
Figure 22 is the sectional view of the major component among Figure 20.
Embodiment
Followingly specify the preferred embodiments of the present invention with reference to accompanying drawing.Yet, must be noted that the present invention is not limited only to these preferred embodiments.
Example 1
Fig. 1 is the longitudinal section of the hermetic type compressor in the preferred embodiments of the present invention 1.Fig. 2 is the amplification sectional view of the major component when compression load does not work in same preferred embodiment.Fig. 3 is the amplification sectional view of the major component when compression load works in same preferred embodiment.Fig. 4 is the sectional view of major component that the relative position of bearing portion in the same preferred embodiment and pressing chamber is shown.Fig. 5 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.
In Fig. 1 to Fig. 3, seal container 101 holds the motor-driven components 104 with stator 102 and rotor 103, and the compressing member 105 that is driven by motor-driven components 104.Include lubricant oil 106 in the bottom of seal container 101.
Axle 110 has main shaft part 111, and forms eccentric axial portion 112 with these main shaft part 111 mass motions prejudicially at an end of main shaft part 111.Main shaft part 111 is fixed in the axle center of rotor 103.Fuel feeding path 113 is formed on the inside and outside of axle 110.The underpart of axle 110 extends into and makes lubricant oil 106 can immerse in the fuel feeding path 113 to prescribed depth.
Cylinder body 114 has pressing chamber 115 and the bearing portion 120 that is arranged to interfix in the cylindrical shape (or approximate circle tubular) of special position.Bearing portion 120 forms cantilever bearings by the end of eccentric axial portion 112 sides in the main shaft part 111 of back shaft 110.
But piston 123 to-and-fro motion ground inserts in the pressing chamber 115.Piston 123 has the wrist pin 125 that is parallel to eccentric axial portion 112, as shown in Fig. 2 and Fig. 3.
Valve plate 150 is assemblied in the end face of cylinder body 114.In cylinder body 114, form cylinder-shaped hole portion 116, so that form pressing chamber 115 with piston 123 and valve plate 150.
As shown in Fig. 2 and Fig. 3, connecting rod 126 is made of big stomidium portion 128, small end hole portion 129 and bar portion 130.Big stomidium portion 128 is coupled on the eccentric axial portion 112, and small end hole portion 129 is connected in piston 123 by wrist pin 125.Eccentric axial portion 112 and piston 123 link together by connecting rod 126 and wrist pin 125.
In this preferred embodiment, when the compression load of compression refrigerant gas worked, with identical in the conventional example, the axle center C of piston 123 was owing to the inclination of axle 110 is tilted.Yet, in this preferred embodiment, by forming pressing chamber 115 with tilt the accordingly axle center D of pressing chamber 115 of the inclination of piston 123.
That is, in this preferred embodiment, when compression load did not work, shown in the amplification sectional view among Fig. 2, the axle center C of piston 123 did not tilt to the pressing chamber 115 that forms by inclination axle center D.On the other hand, when compression load worked, shown in the amplification sectional view among Fig. 3, piston 123 was inclined to and makes the axle center D of pressing chamber 115 and the axle center C of piston 123 to overlap.
The inclination of pressing chamber 115 is described by reference Fig. 4.Bearing portion 120 and pressing chamber 115 are arranged such that first center line 141 in the axle center that bearing portion 120 is shown can intersect each other with second center line 142 that the axle center of pressing chamber 115 is shown.The angle a1 that forms between first center line 141 and second center line 142 is a pi/2 in conventional hermetic type compressor, yet in this preferred embodiment, angle a1 satisfies formula (1) with predetermined angle b1.
In having the hermetic type compressor of this configuration, its operation and Action Specification are as follows.In Fig. 1, the rotor 103 of motor-driven components 104 makes axle 110 rotations.Follow the rotation of axle 110, rotatablely moving of eccentric axial portion 112 is passed to piston 123 by connecting rod 126.Therefore, piston 123 is reciprocating in pressing chamber 115.By the to-and-fro motion of piston 123, refrigerant gas is drawn into the pressing chamber 115 from the unshowned cooling system with refrigeration cycle.Refrigerant gas is compressed once in pressing chamber 115, is discharged in the cooling system once more then.
Similar pump is played by the rotation of axle 110 in the underpart of fuel feeding path 113.By this pumping action, the lubricant oil 106 of seal container 101 bottoms is by fuel feeding path 113 and upwards aspirated, and upwards flatly sprays in whole week in seal container 101.The lubricant oil 106 that sprays is supplied with lube pistons pin 125 and piston 123.
In cantilever bearings, only a side of the main shaft part 111 on the eccentric axial portion 112 of axle 110 supports the compression load of compression refrigerant gas.Therefore, tilt in the gap of axle 110 between main shaft part 111 and bearing portion 120.The axle center 144 of axle 110 the main shaft part 111 that in the gap of bearing portion 120, tilts thus, and angle a1 between second center line 142 in axle center of pressing chamber 115 is shown less than pi/2.
For piston 123 the prizing that prevents that the inclination of axle 110 thus from causing for pressing chamber 115, in this preferred embodiment, with illustrate bearing portion 120 the axle center first center line 141 and angle a1 between second center line in axle center of pressing chamber 115 is shown is set at and is a bit larger tham pi/2.
In Fig. 4, the intersection point of first center line 141 and second center line 142 in the axle center that pressing chamber 115 is shown that the axle center of bearing portion 120 is shown is assumed to O.Based on the gap of bearing portion 120 and main shaft part 111, axle 110 is assumed to c1 with respect to the absolute value at the angle of inclination of bearing portion 120.The value of predetermined angle is angle b1.At this moment, pressing chamber 115 is formed first center line 141 that makes by the axle center that bearing portion 120 is shown and to satisfy formula (1) and formula (3) with second center line, the 142 formed angle a1 that the axle center of pressing chamber 115 is shown.
B1=f (c1); F is about the function of inependent mode c1 (3)
Can adopt experimental value as the occurrence that angle b1 is associated with the absolute value c1 at the angle of inclination of axle 110.Fig. 5 shows the measurement result of the efficient of hermetic type compressor, has wherein prepared four kinds of different cylinder bodies 114 of angle in the axle center of pressing chamber 115, and has assembled these cylinder bodies 114.In Fig. 5, axis of abscissas represent to illustrate pressing chamber 115 the axle center second center line 142 with respect to first center line 141 in the axle center that bearing portion 120 is shown, from the expansion (among Fig. 5, being recited as the angle b1 of pressing chamber) of pi/2 with respect to bearing.Axis of ordinates is represented about the efficient COP of angle b1 (coefficient of performance).That is, Fig. 5 is the second approximation performance plot about the measured value of the efficient COP of angle b1.
Here, line P1 represents that angle b1 is 0 (rad), and the efficient of this moment illustrates the mean value of conventional hermetic type compressor.In this experiment, the absolute value c1 at axle 110 the angle of inclination that is caused by the gap is depicted as about 3.7 * 10 as line Q1 -4(rad).As shown in Figure 5, when angle b1 about 3.7 to 10 * 10 -4When scope (rad) (A) was interior, efficient was very high.Similarly, when angle b1 about 2 to 12 * 10 -4When scope (rad) (B) was interior, efficient was higher than the efficient in the conventional hermetic type compressor.
The absolute value c1 at the angle of inclination of use axle 110 represents the scope of this angle b1, and when in the scope of angle b1 at 1.0c1 to 2.7c1, efficient is very high, and in the time of particularly in the scope of 0.5c1 to 3.3c1, efficient is higher than the efficient in the conventional hermetic type compressor.
Therefore, when with formula (1) expression during by the formed angle a1 of second center line 142 in first center line 141 in the axle center that bearing portion 120 is shown and the axle center that pressing chamber 115 is shown, the absolute value c1 of expected angle b1 and angle satisfies the relation of formula (4).
0.5c1≤b1≤3.3c1 (4)
More preferably, the absolute value c1 of expected angle b1 and angle satisfies the relation of formula (5).
1.0c1≤b1≤2.7c1 (5)
Therefore, the design load of the angle in the axle center by will being defined as pressing chamber 115 by the angle a1 of formula (1) expression, and by being associated with respect to the absolute value c1 at the angle of inclination of bearing portion 120 and predetermined angle b1 is set at more near actual value, can prevent prizing between piston 123 and the pressing chamber 115 more definitely with axle 110.
In addition, in order to raise the efficiency, configuration can be defined as avoiding illustrating intersecting between second center line 142 and first center line 141 that bearing portion 120 is shown in axle center of pressing chamber 115.
Sectional view below by with reference to the upper surface among Fig. 6 of the relative position that bearing portion in this preferred embodiment and pressing chamber are shown is described more specifically this configuration.
With respect to second center line 142 in the axle center that pressing chamber 115 is shown, first center line 141 (among Fig. 6 for a bit) that bearing portion 120 is shown has been offset size " e " abreast, and it generally is called skew.
In Fig. 6, the 3rd center line 143 (among Fig. 6 for a bit) that is parallel to first center line 141 (among Fig. 6 for a bit) in the axle center that bearing portion 120 is shown, that is, be parallel to the line in the axle center of bearing portion 120, intersect each other with second center line 142 in the axle center that pressing chamber 115 is shown.According to experiment, as long as size " e " in 3mm, has then also obtained in this configuration and the result who comes to the same thing shown in Fig. 5.
Therefore, as long as pressing chamber 115 in 3mm, can obtain effect same as described above with respect to the skew (size " e ") of bearing portion 120.That is, when bearing portion 120 and pressing chamber 115 are arranged such that second center line 142 in the axle center that pressing chamber 115 is shown can intersect each other with the 3rd center line 143 that is parallel to first center line 141 in the axle center that bearing portion 120 is shown, can learn following situation.Be illustrated between the 3rd center line 143 and second center line 142 the angle a1 ' that forms (rad) with formula (6), and this moment preferably, the relation of the absolute value c1 satisfiable formula (4) of angle b1 and angle.More preferably, the absolute value c1 of angle b1 and angle should satisfy the relation of formula (5).
a1’＝π/2+b1(rad) (6)
In the cantilever bearings of this preferred embodiment, when piston 123 is positioned at the lower dead centre place, be arranged such that at least a portion of piston 123 can be exposed from cylinder body 114.Particularly, form and make at least 1/3 or more can exposing vertically of overall length of piston 123.
In the rear half stage of suction stroke or in the initial stage of compression stroke, when the effect on the end face 123a of compression load that the pressure by refrigerant gas causes when not being very big at piston 123, axle 110 remains in the gap of main shaft part 111 and bearing portion 120, and it is a lot of can not tilt.Therefore, first center line 141 in the axle center by bearing portion 120 will be shown is set at the relative angle of second center line 142 in the axle center that pressing chamber 115 is shown and is a bit larger tham pi/2, prize increase between piston 123 and the pressing chamber 115, and slippage loss can increase probably.
Yet, in this preferred embodiment, when piston 123 is positioned at the lower dead centre place, be designed so that piston 123 axially at least 1/3 or expose of overall length more.That is, cause the axial length of the piston 123 that prizes to lack size formation, and can suppress prizing between piston 123 and the pressing chamber 115.
Therefore, if piston 123 is positioned near the lower dead centre, then can prevent prizing between piston 123 and the pressing chamber 115.Therefore, higher reliability can be realized, and higher efficient can be realized by reducing slippage loss by the wearing and tearing that reduce piston 123.
Example 2
In preferred embodiment 1, by forming pressing chamber 115 with tilt the accordingly axle center D of pressing chamber 115 of the inclination of piston 123.Yet, in this preferred embodiment, except being configured to of preferred embodiment 1, also in cylinder-shaped hole portion 116, be formed for forming the tapered portion of pressing chamber 115.Therefore, in this preferred embodiment, omit about with preferred embodiment 1 in the explanation of identical configuration, and the different configuration of main explanation and preferred embodiment 1.
Fig. 1 to Fig. 4 is also applicable to this preferred embodiment.Fig. 7 is near the sectional view of the major component of the pressing chamber in this preferred embodiment, shows the state that piston is positioned at the lower dead centre place.Fig. 8 is near the sectional view of the major component of the pressing chamber in the same preferred embodiment, shows the state that piston slides along tapered portion.Fig. 9 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.
In this preferred embodiment,, in cylinder body 114, form cylinder-shaped hole portion 116, so that form pressing chamber 115 with piston 123 and valve plate 150 with identical in preferred embodiment 1.As shown in Figure 7, cylinder-shaped hole portion 116 has the side that a side direction that is positioned at upper dead center from piston 123 is positioned at lower dead centre, and internal diameter increases to Db (＞Dt) tapered portion 117 from Dt.Cylinder-shaped hole portion 116 with the corresponding position, end of pressing chamber 115 sides of the piston 123 that arrives upper dead center, also have the constant straight portion 118 of internal diameter in the section of length L in the axial direction.In the scope of whole overall length, form piston 123 with identical external diameter.
Cylinder body 114 has in the part of the perisporium of cylinder-shaped hole portion 116, that is, the notch that cuts out in upper wall portions 119 so that as shown in Figure 7, exposes anti-pressing chamber 115 sides of piston 123 when piston 123 is positioned at the lower dead centre place.
In this configuration of this preferred embodiment, tilt the accordingly axle center D of pressing chamber 115 of the inclination of the caused piston 123 of inclination of axle 110 forms pressing chamber 115 when working with compression load at compression refrigerant gas, and is formed for forming the tapered portion 117 of pressing chamber 115 in cylinder-shaped hole portion 116.
The configuration that axle center D by the inclination pressing chamber is formed pressing chamber is specifically described.Illustrated in fig. 4 as in preferred embodiment 1, bearing portion 120 and pressing chamber 115 are arranged such that first center line 141 in the axle center that bearing portion 120 is shown can intersect each other with second center line 142 that the axle center of pressing chamber 115 is shown.In the middle of the angle that forms between first center line 141 and second center line 142, the angle between pressing chamber 115 sides of bearing portion 120 sides below first center line 141 and second center line 142 is assumed to a1.In conventional hermetic type compressor, as described in the preferred embodiment 1, angle a1 is a pi/2.In this preferred embodiment, with identical in preferred embodiment 1, the angle of supposing predetermined value is b1, and angle a1 and angle b1 satisfy formula (1).
Below be specifying to the configuration of the tapered portion 117 of the cylinder-shaped hole portion 116 that forms pressing chamber 115 and straight portion 118.As shown in Fig. 7 and Fig. 8, the angle of formation is assumed to d1 between second center line 142 in the axle center of the periphery of piston 123 piston 123 when tapered portion 117 is slided and the axle center that pressing chamber 115 is shown.At this moment, by Fig. 7 and Fig. 8 as can be known, in tapered portion 117 and the angle that forms between second center line 142 in axle center of pressing chamber 115 is shown corresponding to d1.
In having the hermetic type compressor of this configuration, operation and effect and basic identical described in the preferred embodiment 1.Therefore, tilt in the gap of axle 110 between main shaft part 111 and bearing portion 120.Thereby, the axle center 144 of axle 110 the main shaft part 111 that in the gap of bearing portion 120, tilts and angle a1 between second center line 142 in axle center of pressing chamber 115 is shown less than pi/2.
For piston 123 the prizing that prevents to cause for pressing chamber 115 by this inclination of 110, in this preferred embodiment, with illustrate bearing portion 120 the axle center first center line 141 and angle a1 between second center line 142 in axle center of pressing chamber 115 is shown is set at and is a bit larger tham pi/2.
In Fig. 4, with identical in preferred embodiment 1, the intersection point of first center line 141 and second center line 142 in the axle center that pressing chamber 115 is shown that the axle center of bearing portion 120 is shown is assumed to O.Based on the gap of bearing portion 120 and main shaft part 111, axle 110 is assumed to c1 with respect to the absolute value at the angle of inclination of bearing portion 120.The value of predetermined angle is assumed to angle b1, in this preferred embodiment, with identical in preferred embodiment 1, pressing chamber 115 formed first center line 141 that makes by the axle center that bearing portion 120 is shown to satisfy formula (1) and formula (3) with second center line, the 142 formed angle a1 that the axle center of pressing chamber 115 is shown.
As mentioned above, in this preferred embodiment, prevented because piston 123 the prizing that the inclination of axle 110 causes for pressing chamber 115.Simultaneously, also in compression stroke,, suppress slippage loss lower, and, prevented because the generation of the gas leakage that the pressure increase of refrigerant gas causes when piston 123 during near upper dead center position up to intermediate point to the upper dead center side shifting.Therefore, in this preferred embodiment, as shown in Fig. 7 and Fig. 8, the cylinder-shaped hole portion 116 that forms pressing chamber 115 has the straight portion 118 that internal diameter is constant in the axial direction, the corresponding position, upper end portion of pressing chamber 115 sides of piston 123 when it is formed on and is positioned at upper dead center with piston 123.In addition, cylinder-shaped hole portion 116 has the tapered portion 117 that contiguous straight portion 118 forms, and the side that the side direction that its internal diameter is positioned at upper dead center from piston 123 is positioned at lower dead centre increases.
In addition, set the value that obtains on the angle d1 with formation between second center line 142 in predetermined angle b1 axle center C that is added at the periphery of piston 123 piston 123 when tapered portion 117 is slided and the axle center that pressing chamber 115 is shown by being associated with angle c1.That is, pressing chamber 115 is formed make angle b1 and angle d1 and can satisfy formula (7).
(b1+d1)=f ' is (c1); F ' is about the function of inependent mode c1 (7)
Therefore, in this preferred embodiment, as the value of predetermined angle b1, the perhaps value that the set angle d1 addition of angle b1 and tapered portion 117 is obtained can adopt experimental value as the occurrence that is associated with the absolute value c1 at the angle of inclination of axle 110.Fig. 9 shows the measurement result of the efficient of the hermetic type compressor in this preferred embodiment, has wherein prepared to illustrate the different several cylinder bodies 114 of angle of second center line 142 in the axle center of pressing chamber 115, and has assembled these cylinder bodies 114.
Promptly, with illustrate pressing chamber 115 the axle center second center line 142 with respect to first center line 141 in the axle center that bearing portion 120 is shown, from the angle d1 sum (b1+d1) of the start point b1 of pi/2 and tapered portion 117 absolute value c1 divided by the angle of inclination of axle 110, and on axis of abscissas, draw the dimensionless number that is obtained.On the axis of ordinates expression with axis of abscissas on the corresponding efficient COP of each angle.That is, Fig. 9 is the second approximation performance plot at each measured value of the efficient at (b1+d1)/c1 place.
Here, the efficient at 0 value place on axis of abscissas is illustrated in the mean value in the configuration that does not have tapered portion 117 in the conventional hermetic type compressor.The absolute value c1 at the angle of inclination of the axle 110 in the gap in this experiment is about 3.7 * 10 -4(rad).Therefore, in Fig. 9, these values are represented by line P2 and line Q2.
As shown in Figure 9, when the value of (b1+d1)/c1 was in about scope of 1 to 3.2 (A), efficient was very high.Also as can be known when the value of (b1+d1)/c1 is in about scope of 0.3 to 4 (B), efficient is higher than conventional hermetic type compressor.
Therefore, when second center line 142 in the axle center that pressing chamber 115 is shown with formula (1) during with respect to the angle a1 of first center line 141 in the axle center that bearing portion 120 is shown, angle b1 and angle c1 should preferably satisfy the relation of formula (8).
0＜b1≤2.5c1 (8)
Simultaneously, by angle b1 is set at do not comprise 0 (rad) on the occasion of, particularly in compression stroke, can prevent effectively when axle 110 prizing between the straight portion 118 during earth tilt and the piston 123 largely in the gap of main shaft part 111 and bearing portion 120.In addition, by angle b1 is set at 2.5c1 or littler, in the rear half stage of suction stroke or in the initial stage of compression stroke, when not tilting in the gap of axle 110 in main shaft part 111 and bearing portion 120 when a lot, can prevent from effectively between piston 123 and pressing chamber 115, to produce and prize.
Simultaneously, by when the axle center C of the periphery of piston 123 piston 123 when tapered portion 117 is slided and the preferably satisfied formula (9) relevant with angle d1 of second center line, 142 formed angle d1 in the axle center that pressing chamber 115 is shown with angle b1, angle c1.
0.3c1≤(b1+d1)≤4c1 (9)
More preferably, angle b1, angle d1 and angle c1 should have the relation that satisfies formula (10).
c1≤(b1+d1)≤3.2c1 (10)
Here, illustrate the axle center 142 of pressing chamber 115 is the effect greater than pi/2 with respect to the angular setting in the axle center 141 of bearing portion 120, and the effect that forms tapered portion 117 in connecting rod 126 sides of pressing chamber 115.
At first, with illustrate pressing chamber 115 the axle center second center line 142 with respect to the angular setting of first center line 141 in the axle center that bearing portion 120 is shown for greater than the effect of pi/2 with illustrated identical in preferred embodiment 1.That is, can prevent piston that inclination caused 123 the prizing for pressing chamber 115 of the caused axle 110 of compression load by the cantilever bearings compression refrigerant gas time in the gap of bearing portion 120 effectively.
Yet, when piston 123 in pressing chamber 115 during to-and-fro motion because the slip between the inner circle wall of the periphery of piston 123 and pressing chamber 115, it is relatively large that slippage loss becomes.
For the slippage loss between the inner circle wall of the periphery that reduces piston 123 and pressing chamber 115, in this preferred embodiment, upper dead center side at pressing chamber 115 is provided with the straight portion 118 that internal diameter is constant in the axial direction, and is formed with the tapered portion of being arranged to from the increase of upper dead center side direction lower dead centre side internal diameter 117 in connecting rod 126 sides of pressing chamber 115.
Therefore, in compression stroke,, produce gas leakage (that is the phenomenon of in pressing chamber 115, leaking the gap of refrigerant compressed between the inwall of the periphery of piston 123 and pressing chamber 115) hardly up to intermediateness to the upper dead center side shifting.In addition, the slip resistance of piston 123 (slippage loss) becomes littler.In addition, be performed until in the state of piston 123 near upper dead center, compare, can reduce the generation of the gas leakage of the refrigerant gas that causes by the air pressure increase with the situation that on whole length, forms tapered portion 117 in compression stroke.
Here, in compression stroke, be contemplated that the periphery of piston 123 can be slided along tapered portion 117.As shown near the sectional view of the major component the pressing chamber among Fig. 8, when the periphery of piston 123 along tapered portion 117 on the gravitational direction during to lower slider, the axle center C of piston 123 is with respect to the rake ratio pi/2 big (b1+d1) of first center line 141 in the axle center that bearing portion 120 is shown.Therefore, not only considering angle b1 but also considering under the situation of angle d1 of tapered portion 117, can consider by and based on the gap between bearing portion 120 and the main shaft part 111, axle 110 is optimized with respect to the relation of the absolute value c1 at the angle of inclination of bearing portion 120.
As an alternative, under the situation of the angle d1 that only considers tapered portion 117, if by and based on the gap between bearing portion 120 and the main shaft part 111, axle 110 designs with respect to the relation of the absolute value c1 at the angle of inclination of bearing portion 120, if the upper dead center side at pressing chamber 115 is provided with the straight portion 118 that internal diameter is constant vertically, then for the situation of between straight portion 118 and piston 123, sliding, can not prevent prizing between the piston 123 that causes for the inclination of bearing portion 120 by axle 110 and the pressing chamber 115.
With the axle center C of piston 123 for the inclination of first center line 141 in the axle center that bearing portion 120 is shown when in conventional hermetic type compressor, similarly remaining on pi/2, with based on the gap of bearing portion 120 and main shaft part 111, axle 110 designs relatively with respect to the absolute value c1 at the angle of inclination of bearing portion 120 under the situation of angle d1 of tapered portion 117, if the angle d1 of tapered portion 117 is bigger, the behavior instability of piston 123 in pressing chamber 115 then, and noise may increase.Simultaneously, the maintenance of the lubricant oil 106 between piston 123 and the pressing chamber 115 becomes insufficient, and the leakage of refrigerant gas may increase.
On the contrary, if the angle value d1 of tapered portion 117 is less, the effect that then reduces the slippage loss between the inner circle wall of the periphery of piston 123 and pressing chamber 115 is weakened.
Therefore, can prevent prizing between the piston 123 that causes for the inclination of bearing portion 120 by axle 110 and the pressing chamber 115.Simultaneously, also can reduce effectively in compression stroke up to slip resistance (slippage loss) to the piston 123 of the intermediateness of upper dead center side shifting.In addition, be performed until in the state of piston 123 near upper dead center position, reduced the generation of the gas leakage of the refrigerant gas that causes by the air pressure increase in compression stroke.In order to satisfy these requirements, be greater than pi/2 with the axle center of pressing chamber 115 with respect to the angular setting in the axle center of bearing portion 120, connecting rod 126 sides at pressing chamber 115 are provided with tapered portion 117 simultaneously, make to obtain synergy.
Yet, only by with the axle center of pressing chamber 115 with respect to the angular setting in the axle center of bearing portion 120 for tapered portion 117 being set greater than pi/2 and in connecting rod 126 sides of pressing chamber 115, can not complementary problem each other.Promptly, under angle d1 both situation of the axle center of considering pressing chamber 115 with respect to the angle a1 in the axle center of bearing portion 120 and tapered portion 117, angle b1, angle d1 and angle c1 can be restricted to the relation that satisfies formula (9) or formula (10), and can by with based on the gap between bearing portion 120 and the main shaft part 111, axle 110 is associated for the absolute value c1 at the angle of inclination of bearing portion 120 and is set to more near actual value, and realize above effect.
At this moment, additionally, when angle b1 and angle d1 satisfied concerning of formula (11), according to experimental result, effect further improved, and reliability and efficient are than much higher in the conventional hermetic type compressor.
0.5b1≤d1≤1.5b1 (11)
If the angle d1 of tapered portion 117 is less than 0.5 times of angle b1, the effect that then reduces the slippage loss between the inner circle wall of the periphery of piston 123 and pressing chamber 115 weakens, on the contrary, if the angle d1 of tapered portion 117 is greater than 1.5 times of angle b1, then cause the noise increase, and be intended to here be optimized from the angle of two specific characters owing to the behavior of piston 123 in pressing chamber 115 is unstable.
In this preferred embodiment, similarly, with identical in preferred embodiment 1, in order to obtain more high efficiency, parts can be arranged such that second center line 142 in the axle center that pressing chamber 115 is shown can be not crossing with first center line 141 in the axle center that bearing portion 120 is shown.In this case, equally in this preferred embodiment, with by with reference to Fig. 6 identical described in the preferred embodiment 1, angle a1 ' and angle b1 can be restricted to and satisfy formula (6).
In this preferred embodiment, when piston 123 was positioned at the lower dead centre place, the part of piston 123 was formed from cylinder body 114 and exposes at least equally.More specifically, 1/3 of the overall length of piston 123 with the upper edge it axially exposes.Therefore, and identical described in the preferred embodiment 1, in this preferred embodiment, similarly, can prevent prizing between near when piston 123 is lower dead centre piston 123 and the pressing chamber 115.
In this preferred embodiment, simultaneously, on the inner circle wall of the pressing chamber 115 corresponding, form the straight portion 118 that internal diameter is constant vertically with the upper end portion of pressing chamber 115 sides of piston 123 when piston 123 is positioned at upper dead center.Yet, under the situation that does not form straight portion 118, as long as it is promptly applicable to be provided with tapered portion 117 the present invention.Promptly, if only form tapered portion 117, although tend to descend from the leakage increase and the efficient of the refrigerant gas of pressing chamber 115, however can by by with based on the gap between bearing portion 120 and the main shaft part 111, axle 110 is associated for the absolute value c1 of the inclination of bearing portion 120 and design that angle d1 is set at more near actual value solves these problems.
Example 3
In preferred embodiment 1 and 2, by forming pressing chamber 115 with tilt the accordingly axle center of pressing chamber 115 of the inclination of piston 123.Yet, in this preferred embodiment, cause that by the inclination of axle 110 tilt the accordingly axle center of pin-and-hole of the inclination of incline link forms pin-and-hole when working with compression load at compression refrigerant gas.
Figure 10 is the longitudinal section of the hermetic type compressor in this preferred embodiment.Figure 11 is the amplification sectional view of the major component when compression load does not work in same preferred embodiment.Figure 12 is the amplification sectional view of the major component when compression load works in same preferred embodiment.Figure 13 is the sectional view of major component that the relative position of piston in the same preferred embodiment and pin-and-hole is shown.Figure 14 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.Identical in the basic configuration of the hermetic type compressor of this preferred embodiment and preferred embodiment 1 and 2, but will describe once more.
In Figure 10 to Figure 12, seal container 101 holds the motor-driven components 104 with stator 102 and rotor 103, and the compressing member 105 that is driven by motor-driven components 104.Include lubricant oil 106 in the bottom of seal container 101.
Axle 110 has main shaft part 111, and forms eccentric axial portion 112 with these main shaft part 111 mass motions prejudicially at an end of main shaft part 111.Main shaft part 111 is fixed in the axle center of rotor 103.Fuel feeding path 113 is formed on the inside and outside of axle 110.The underpart of axle 110 extends into and makes lubricant oil 106 can immerse in the fuel feeding path 113 to prescribed depth.
Cylinder body 114 has pressing chamber 115 and the bearing portion 120 that is arranged to interfix in the approximate circle tubular of special position.Bearing portion 120 forms cantilever bearings by the end of eccentric axial portion 112 sides in the main shaft part 111 of back shaft 110.
But piston 123 to-and-fro motion ground inserts in the pressing chamber 115.Piston 123 has pin-and-hole 124, and wrist pin 125 is inserted and secured in the pin-and-hole 124.
As shown in Figure 11 and Figure 12, connecting rod 126 is made of big stomidium portion 128, small end hole portion 129 and bar portion 130.Big stomidium portion 128 is coupled on the eccentric axial portion 112.Small end hole portion 129 is connected in piston 123 by wrist pin 125.Eccentric axial portion 112 and piston 123 link together by connecting rod 126 and wrist pin 125.
In this preferred embodiment, when the compression load of compression refrigerant gas worked, connecting rod 126 was also owing to the inclination of axle 110 is tilted.Yet, by forming pin-and-hole 124 with tilt the accordingly axle center of pin-and-hole 124 of the inclination of connecting rod 126.
The state of this inclination is described with reference to Figure 11 and Figure 12.In Figure 11, compression load does not work, and this illustrates the amplification sectional view of state of the axle center C of the piston 123 that forms by the axle center with respect to the axle center D inclination pin-and-hole 124 of pressing chamber 115.In Figure 12, compression load works, and this illustrates the amplification sectional view of the state of the piston 123 that makes that the axle center D of pressing chamber 115 can overlap with the axle center C of piston 123.
Figure 13 illustrates the inclination of pin-and-hole 124, wherein, at first center line 141 of the axle center C that piston 123 is shown and the angle a2 that forms between second center line 142 in axle center of pin-and-hole 124 is shown, in conventional hermetic type compressor, be pi/2, but in this preferred embodiment, be defined as to satisfy formula (2) with predetermined angle b2.
In having the hermetic type compressor of this configuration, its operation and Action Specification are as follows.The rotor 103 of motor-driven components 104 makes axle 110 rotations.Follow the rotation of axle 110, rotatablely moving of eccentric axial portion 112 is passed to piston 123 by connecting rod 126.Therefore, piston 123 to-and-fro motion in pressing chamber 115.By the to-and-fro motion of piston 123, refrigerant gas is drawn into the pressing chamber 115 from unshowned cooling system, and is compressed once, and is discharged in the cooling system once more.
Similar pump is played by the rotation of axle 110 in the underpart of fuel feeding path 113.By this pumping action, the lubricant oil 106 of seal container 101 bottoms is by fuel feeding path 113 and upwards aspirated, and upwards flatly sprays in whole week in seal container 101.The lubricant oil 106 that sprays is supplied with lube pistons pin 125 and piston 123.
In cantilever bearings, only a side of the main shaft part 111 on the eccentric axial portion 112 of axle 110 supports the compression load of compression refrigerant gas.Therefore, tilt in the gap of axle 110 between main shaft part 111 and bearing portion 120.Thereby the relative angle between the axle center 144 of the main shaft part 111 of the axle 110 that tilts in the gap of bearing portion 120 and the axle center D of pressing chamber 115 is less than pi/2.
For piston 123 the prizing that prevents to cause for pressing chamber 115 by this inclination of 110, in this preferred embodiment, with illustrate piston 123 the axle center first center line 141 and relative angle between second center line 142 in axle center of pin-and-hole 124 is shown is set at and is a bit larger tham pi/2.
In Figure 12 and Figure 13, the intersection point of first center line 141 and second center line 142 in the axle center that pin-and-hole 124 is shown that the axle center C of piston 123 is shown is assumed to O.Be assumed to c2 based on the axle center 144 gap, main shaft part 111 of bearing portion 120 and main shaft part 111 with respect to the absolute value at the angle of inclination in the axle center of bearing portion 120.The value of predetermined angle is angle b2, and pin-and-hole 124 is formed first center line 141 that makes by the axle center C that piston 123 is shown and can satisfies formula (2) and formula (12) with second center line, the 142 formed angle a2 that the axle center of pin-and-hole 124 is shown.
B2=f (c2); F is about the function of inependent mode c2 (12)
Can adopt experimental value as the occurrence that predetermined angle b2 is associated with the absolute value c2 at the angle of inclination of axle 110.Figure 14 shows the measurement result of the efficient of hermetic type compressor, has wherein prepared the different piston 123 of angle in the axle center of pin-and-hole 124, and has assembled these pistons 123.That is, axis of abscissas represent to illustrate pin-and-hole 124 the axle center second center line 142 with respect to first center line 141 in the axle center that piston 123 is shown, from the expansion (among Figure 14, being recited as the angle b2 of pin-and-hole axle center) of pi/2 with respect to piston axes.Axis of ordinates is represented the efficient COP with respect to angle b2.That is, Figure 14 is the second approximation performance plot about the measured value of the efficient COP of angle b2.
Here, be the mean value that the efficient at 0 place illustrates conventional hermetic type compressor in that angle b2 is shown by line P3.In this experiment, the absolute value c2 at axle 110 the angle of inclination that is caused by the gap is about 3.7 * 10 -4As shown in Figure 14, when angle b2 about 3.7 to 10 * 10 -4Scope (A) when interior, efficient is very high.Similarly, when angle b2 about 2 to 12 * 10 -4Scope (B) when interior, efficient is higher than the efficient in the conventional hermetic type compressor.
The absolute value c2 at the angle of inclination of use axle 110 represents the scope of this angle b2, and when in the scope of angle b2 at 1.0c2 to 2.7c2, efficient is very high, and in the time of particularly in the scope of 0.5c2 to 3.3c2, efficient is higher than the efficient in the conventional hermetic type compressor.
Therefore, when with formula (2) expression during by the formed angle a2 of second center line 142 in first center line 141 in the axle center that piston 123 is shown and the axle center that pin-and-hole 124 is shown, the absolute value c2 of expected angle b2 and angle satisfies the relation of formula (13).
0.5c2≤b2≤3.3c2 (13)
More preferably, expected angle b2 and angle c2 satisfy the relation of formula (14).
1.0c2≤b2≤2.7c2 (14)
Therefore, in this preferred embodiment, the design load of the angle in the axle center by will being defined as pin-and-hole 124 by the angle a2 of formula (2) expression, and by being associated with respect to the absolute value c2 at the angle of inclination of bearing portion 120 and predetermined angle b2 is set at more near actual value, can prevent prizing between piston 123 and the pressing chamber 115 with axle 110.
In addition, in the cantilever bearings of this preferred embodiment, when piston 123 is positioned at the lower dead centre place, be designed so that at least a portion of piston 123 can be exposed from cylinder body 114.More specifically, piston 123 axially on can the exposing more than 1/3 of overall length.
In the rear half stage of suction stroke or in the initial stage of compression stroke, when the effect on the end face 123a of compression load that the pressure by refrigerant gas causes when not being very big at piston 123, axle 110 remains in the gap of main shaft part 111 and bearing portion 120, and it is a lot of can not tilt.Therefore, first center line 141 in the axle center by piston 123 will be shown is set at the relative angle of second center line 142 in the axle center that pin-and-hole 124 is shown and is a bit larger tham pi/2, prize increase between piston 123 and the pressing chamber 115, and slippage loss can increase probably.
Yet, in this preferred embodiment, when piston 123 is positioned at the lower dead centre place, be designed so that piston 123 axially at least 1/3 or more can exposing of overall length.That is, cause the axial length of the piston 123 that prizes to lack size formation, and can suppress prizing between piston 123 and the pressing chamber 115.
Therefore, if piston 123 is positioned near the lower dead centre, then can prevent prizing between piston 123 and the pressing chamber 115.Therefore, higher reliability can be realized, and higher efficient can be realized by reducing slippage loss by the wearing and tearing that reduce piston 123.
In this preferred embodiment, piston 123 in the vertical directions are asymmetric, make in assembling process, can easily distinguish about.Particularly, be formed with judgement hole 146a on the top of piston 123.Make this judgement hole 146a can be in upside by being assembled into, not built-up piston 123 upside down.Therefore, can obtain the effect that preventing between piston 123 and the pressing chamber 115 prizes definitely.
In this preferred embodiment similarly, and identical described in the preferred embodiment 2, by in cylinder-shaped hole portion 116, being formed for forming the tapered portion 117 of pressing chamber 115, obtained with preferred embodiment 2 in identical effect.That is, except at Figure 10 to illustrated in fig. 13 being configured to, by the configuration shown in application drawing 7 and Fig. 8, obtained characteristic as shown in Figure 9.In Fig. 7 to Fig. 9, with identical parts in identical designated and the preferred embodiment 2, and use with preferred embodiment 2 in identical description of symbols angle.In this preferred embodiment, set by being associated with angle c2 gained on the angle d2 that forms between second center line 142 with predetermined angle b2 axle center C that is added at the periphery of piston 123 piston 123 when tapered portion 117 is slided and the axle center that pressing chamber 115 is shown with.With pressing chamber 115 form make angle b2 and angle d2 and can satisfy formula (15).
(b2+d2)=f " (c2); F " be function (15) about inependent mode c2
In this preferred embodiment, similarly, as the predetermined angle d2 sum of predetermined angle b2 or angle b2 and tapered portion 117, the concrete numerical value that can adopt the experimental value conduct to be associated with the absolute value c2 at the angle of inclination of axle 110.By with preferred embodiment 2 in identical experiment, obtained with Fig. 9 in identical measurement result.
Therefore, in this preferred embodiment, similarly, the relation of the preferably satisfied formula (16) about angle b2, angle c2 and angle d2 of the angle d2 that between second center line 142 in the axle center C of the periphery of piston 123 piston 123 when tapered portion 117 is slided and the axle center that pressing chamber 115 is shown, forms.
0.3c2≤(b2+d2)≤4c2 (16)
In addition, angle b2, angle d2 and angle c2 should preferably satisfy the relation of formula (17).
c2≤(b2+d2)≤3.2c2 (17)
In addition, when angle b2 and angle d2 satisfy formula (18), obtain with preferred embodiment 2 in identical effect, and reliability and efficient are than much higher in the conventional hermetic type compressor.
0.5b2≤d2≤1.5b2 (18)
Example 4
In preferred embodiment 1 and 2, by forming pressing chamber 115 with tilt the accordingly axle center of pressing chamber 115 of the inclination of piston 123.In preferred embodiment 3, cause that by the inclination of axle 110 tilt the accordingly axle center of pin-and-hole 124 of the inclination of incline link 126 forms pin-and-hole 124 when working with compression load at compression refrigerant gas.Yet in this preferred embodiment, the inclination of the axle 110 when working with the compression load of compression refrigerant gas is accordingly with respect to the axle center of inclination small end hole, the axle center portion 129 of big stomidium portion 128.
The basic configuration of the hermetic type compressor of this preferred embodiment is identical with basic configuration in preferred embodiment 3 illustrated in fig. 10.Figure 15 is the amplification sectional view of the major component when compression load does not work in this preferred embodiment.Figure 16 is the amplification sectional view of the major component when compression load works in same preferred embodiment.Figure 17 is the sectional view of major component that the relative position of the big stomidium portion of the connecting rod in the same preferred embodiment and small end hole portion is shown.Figure 18 is the performance plot that illustrates based on the result of experiment of same preferred embodiment.
, and therefore omit identical in the explanation of the overall arrangement of this preferred embodiment and the preferred embodiment 3 with reference to Figure 10, Figure 15 and Figure 16.In this preferred embodiment, as mentioned above, axle 110 the inclination when working with the compression load of compression refrigerant gas is corresponding, with respect to the axle center of inclination small end hole, the axle center portion 129 of big stomidium portion 128.
The state of this inclination is described with reference to Figure 15 and Figure 16.Figure 15 shows the amplification sectional view of the axle center C of piston 123 when compression load does not work with respect to the state of the axle center D of pressing chamber 115.Figure 16 shows and makes the amplification sectional view of state of piston 123 that the axle center C of the axle center D of when compression load works pressing chamber 115 and piston 123 can overlap and connecting rod 126.
Figure 17 illustrates the tilt relationship in the axle center of the axle center of big stomidium portion 128 and small end hole portion 129.As shown in Figure 17, at first center line 141 in the axle center that big stomidium portion 128 is shown and illustrate in the middle of the angle that forms between second center line 142 in axle center of small end hole portion 129, the angle of formation is assumed to a3 between eccentric axial portion 112 sides (anti-main shaft part 111 sides) of eccentric axial portion 112 sides above first center line 141 (anti-main shaft part 111 sides) and second center line 142 or line 143 tops.Based on the gap between bearing portion 120 and the main shaft part 111, axle 110 is assumed to c3 with respect to the absolute value at the angle of inclination of bearing portion 120.In conventional hermetic type compressor, angle a3 is 0.In this preferred embodiment, angle a3 is limited by formula (19).
0.5c3≤a3≤3.3c3 (19)
That is, the axle center of big stomidium portion 128 and the axle center of small end hole portion 129 along with from eccentric axial portion 112 sides (top) to the advancing of main shaft part 111 sides (below), tilt slightly along close direction.
In having the hermetic type compressor of this configuration, basic operation and effect and are omitted its explanation with identical in preferred embodiment 3.In this preferred embodiment, similarly, in cantilever bearings, the compression load during compression refrigerant gas is only supported by the main shaft part 111 on the side of the eccentric axial portion 112 of axle 110.Thereby axle 110 tilts in the gap of main shaft part 111 and bearing portion 120.
The relative angle of the axle center 144 of the main shaft part 111 of the axle 110 that therefore, tilts in the gap of bearing portion 120 and the axle center D of pressing chamber 115 is less than pi/2.
For piston 123 the prizing that prevents to cause for pressing chamber 115 by this inclination of 110, in this preferred embodiment, with illustrate big stomidium portion 128 the axle center first center line 141 and relative angle between second center line 142 in axle center of small end hole portion 129 is shown is set at and is a bit larger tham 0.
In Figure 16 and Figure 17, big stomidium portion 128 and small end hole portion 129 are formed the angle a3 that makes between second center line 142 in first center line 141 and the axle center that small end hole portion 129 is shown in axle center that big stomidium portion 128 is shown, and can satisfy formula (15) based on the axle center 144 gap, main shaft part 111 of bearing portion 120 and main shaft part 111 with respect to the absolute value c3 at the angle of inclination in the axle center of bearing portion 120.In Figure 17, for easy to understand angle a3, indicate the line 143 parallel, and represent this line 143 and angle between first center line 141 in axle center of big stomidium portion 128 is shown with angle a3 with second center line 142 in the axle center that small end hole portion 129 is shown.
Can adopt experimental value as the occurrence that angle a3 is associated with the absolute value c3 at the angle of inclination of axle 110.Figure 18 shows the measurement result of the efficient COP of hermetic type compressor, has wherein prepared the connecting rod 126 that the relative angle a3 between the axle center of the axle center of big stomidium portion 128 and small end hole portion 129 changes, and has assembled these connecting rods 126.That is, at first center line 141 of drawing the axle center that big stomidium portion 128 is shown on the axis of abscissas and angle between second center line 142 in axle center of the small end hole portion 129 angle a3 of the axle center of the axle center of the big stomidium portion of connecting rod and small end hole portion (in the Figure 18 for) is shown.On axis of ordinates, draw efficient COP for each angle a3 value.That is, Figure 18 is the second approximation performance plot at each measured value of the efficient COP of each angle a3 value.
Here, be the mean value that the efficient at 0 place illustrates conventional hermetic type compressor in that angle a3 is shown by line P4.The absolute value c3 at axle 110 the angle of inclination that is caused by the gap by in this experiment shown in the line Q4 is about 3.7 * 10 -4As shown in Figure 18, when angle a3 about 3.7 to 10 * 10 -4Scope (A) when interior, efficient is very high.Similarly, when angle a3 about 2 to 12 * 10 -4Scope (B) when interior, efficient is higher than the efficient in the conventional hermetic type compressor.
The absolute value c3 at the angle of inclination of use axle 110 represents the scope of this angle a3, and when in the scope of angle a3 at 1.0c3 to 2.7c3, efficient is very high, and in the time of particularly in the scope of 0.5c3 to 3.3c3, efficient is higher than the efficient in the conventional hermetic type compressor.
Therefore, first center line 141 by the axle center that big stomidium portion 128 is shown should preferably satisfy the relation of formula (19) with angle a3 and the angle c3 that second center line 142 that the axle center of small end hole portion 129 is shown forms.More preferably, expected angle a3 and angle c3 satisfy the relation of formula (20).
1.0c3≤a3≤2.7c3 (20)
Yet, if angle a3 sets too smallly for angle c3, particularly in compression stroke, then can not prevent when axle 110 inclination prizing between straight portion 118 and the piston 123 when a lot of in the gap of main shaft part 111 and bearing portion 120, perhaps on the contrary, if angle a3 sets too much for angle c3, then in the rear half stage of suction stroke or in the initial stage of compression stroke, when not tilting in the gap of axle 110 in main shaft part 111 and bearing portion 120 when a lot, can not prevent prizing between piston 123 and the pressing chamber 115.
Therefore, in this preferred embodiment, by explicitly the angle a3 in the axle center of the axle center of big stomidium portion 128 and small end hole portion 129 being defined as more near actual value with respect to the absolute value c3 at the angle of inclination of bearing portion 120, can prevent prizing between piston 123 and the pressing chamber 115 with axle 110.
In addition, in the cantilever bearings of this preferred embodiment, when piston 123 is positioned at the lower dead centre place, be designed so that at least a portion of piston 123 can be exposed from cylinder body 114.More specifically, piston 123 axially on can the exposing more than 1/3 of overall length.
In this preferred embodiment, with identical in preferred embodiment 3, in the rear half stage of suction stroke or in the initial stage of compression stroke, first center line 141 in the axle center by big stomidium portion 128 will be shown is set at the relative angle of second center line 142 in the axle center that small end hole portion 129 is shown and is a bit larger tham 0, prize increase between piston 123 and the pressing chamber 115, and slippage loss can increase probably.
Yet, in this preferred embodiment, when piston 123 is positioned at the lower dead centre place, be designed so that piston 123 axially at least 1/3 or more can exposing of overall length.That is, cause the axial length of the piston 123 that prizes to lack size formation, and can suppress prizing between piston 123 and the pressing chamber 115.
Therefore, if piston 123 is positioned near the lower dead centre, then can prevent prizing between piston 123 and the pressing chamber 115.Therefore, higher reliability can be realized, and higher efficient can be realized by reducing slippage loss by the wearing and tearing that reduce piston 123.
In this preferred embodiment, connecting rod 126 in the vertical directions are asymmetric, make in assembling process, can easily distinguish about.Particularly, be formed with the protruding 146b of judgement on the top of connecting rod 126.Make this judge that protruding 146b can be in upside by being assembled into, can not assemble connecting rod 126 upside down.Therefore, can obtain the effect that preventing between piston 123 and the pressing chamber 115 prizes definitely.
For higher efficient, parts can be arranged such that the center line in the axle center that pressing chamber 115 is shown can not intersect with the axle center of bearing portion 120.In this case, similarly, with identical in preferred embodiment 1, as long as pressing chamber 115 from the skew of bearing portion 120 in 3mm, can obtain with this preferred embodiment in identical effect.
In this preferred embodiment, similarly, and identical described in preferred embodiment 2 and 3, by in cylinder-shaped hole portion 116, being formed for forming the tapered portion 117 of pressing chamber 115, obtained with preferred embodiment 2 and 3 in identical effect.
Therefore, in this preferred embodiment, similarly, the relation of the preferably satisfied formula (21) about predetermined angle b3, angle c3 and angle d3 of the angle d3 that forms between second center line 142 in the axle center of piston 123 C and the axle center that pressing chamber 115 is shown when tapered portion 117 is slided when the periphery of piston 123.
0.3c3≤(b3+d3)≤4c3 (21)
In addition, angle b3, angle d3 and angle c3 should preferably satisfy the relation of formula (22).
c3≤(b3+d3)≤3.2c3 (22)
In addition, when angle b3 and angle d3 satisfy formula (23), obtain with preferred embodiment 2 in identical effect, and reliability and efficient are than much higher in the conventional hermetic type compressor.
0.5b3≤d3≤1.5b3 (23)
Example 5
Figure 19 is to use in the preferred embodiment 1 to 4 schematic configuration diagram of the refrigerator refrigerators any hermetic type compressor, in the preferred embodiments of the present invention 5 of explanation.In Figure 19, the refrigerator refrigerator 200 of this preferred embodiment comprises a plurality of storerooms 202 in the front that is arranged on casing 201, and the machine room 203 that is arranged on the back side.Machine room 203 holds the hermetic type compressor 204 described in preferred embodiment 1 to 4.Hermetic type compressor 204 is by managing the 206 refrigeration cycle element 205 that are connected in such as condenser.Hermetic type compressor 204 is controlled by control gear 207, and moves suitable refrigeration cycle.Therefore, according to this preferred embodiment, high reliability and high efficiency refrigerator refrigerator have been obtained.
Industrial usability
Therefore as described herein, hermetic type compressor of the present invention can be realized high reliability and high efficiency, is applicable to the freezing and refrigerating equipment of the running refrigerating circulation of air-conditioner for example or automatic vending machine.
Reference numerals list
101 closed containers
102 stators
103 rotors
104 motor-driven components
105 compressing members
106 lubricating oil
110 axles
111 main shaft part
112 eccentric axial portion
113 fuel feeding paths
114 cylinder bodies
115 discharge chambes
116 cylinder-shaped hole sections
117 tapered portion
118 straight portion
120 bearing portions
123 pistons
The 123a end face
124 pin-and-holes
125 piston pins
126 connecting rods
128 big stomidium sections
129 small end hole portions
130 bar portions
141 first center lines
142 second center lines
143 the 3rd center lines
The axle center of 144 main shaft part
146a judges the hole
146b judges projection
150 valve plates
200 refrigerator refrigerators
201 casings
202 storerooms
203 machine rooms
204 hermetic compressors
205 refrigeration cycle element
206 pipes
207 control gear

Claims (26)

1. hermetic type compressor comprises:
The compressing member that is contained in the motor-driven components in the seal container and drives by described motor-driven components,
Wherein, described compressing member comprises: axle, and it has the main shaft part by described motor-driven components rotation and driving, and is formed on an end of described main shaft part and the eccentric axial portion that described main shaft part is integrally moved; Bearing portion, it forms cantilever bearings by the described main shaft part that supports described axle; Cylinder body, it is arranged to be fixed on the special position in the described bearing portion, and forms columnar pressing chamber; Be inserted into can be in described pressing chamber pistons reciprocating; And the connecting rod that is used to connect described eccentric axial portion and described piston, and, the 3rd center line that described bearing portion and described pressing chamber are arranged such that first center line in the axle center that described bearing portion is shown or are parallel to described first center line can intersect each other with second center line in the axle center that described pressing chamber is shown
The angle a1 (rad) and the predetermined angle b1 (rad) that are formed by described first center line or described the 3rd center line and described second center line satisfy formula (1), and by setting described angle b1 with being associated with respect to the absolute value c1 (rad) at the angle of inclination of described bearing portion based on the axle gap between described bearing portion and the described main shaft part, described.
a1＝π/2+b1(rad) (1)
2. hermetic type compressor as claimed in claim 1,
Wherein said angle b1 be set to described angle absolute value c1 more than 0.5 times to below 3.3 times.
3. hermetic type compressor as claimed in claim 1,
Wherein said angle b1 be set to described angle absolute value c1 more than 1.0 times to below 2.7 times.
4. hermetic type compressor as claimed in claim 1,
Wherein said angle b1 be set to described angle absolute value c1 below 2.5 times do not comprise 0 (rad) on the occasion of, and described pressing chamber has and is formed the tapered portion that a side internal diameter that a side direction that is positioned at upper dead center from described piston is positioned at lower dead centre increases, and the angle d1 that between the axle center of the axle center of described piston and described pressing chamber, forms during along described tapered portion slip when the periphery of described piston and the described angle b1 sum absolute value c1 that is set to described angle more than 0.3 times to below 4 times.
5. hermetic type compressor as claimed in claim 4,
Wherein said angle b1 and described angle d1 sum be set to described angle absolute value c1 more than 1.0 times to below 3.2 times.
6. hermetic type compressor as claimed in claim 5,
Wherein said angle d1 be set to described angle b1 more than 0.5 times to below 1.5 times.
7. hermetic type compressor as claimed in claim 4,
The straight portion that also is included in corresponding position, the upper end portion of the described pressing chamber side of described piston when being positioned at upper dead center, forms adjacent to described tapered portion with described piston.
8. hermetic type compressor as claimed in claim 1,
Wherein when described piston was positioned at lower dead centre, at least a portion of described piston was exposed from described cylinder body.
9. hermetic type compressor comprises:
The compressing member that is contained in the motor-driven components in the seal container and drives by described motor-driven components,
Wherein, described compressing member comprises: axle, and it has the main shaft part by described motor-driven components rotation and driving, and is formed on an end of described main shaft part and the eccentric axial portion that described main shaft part is integrally moved; Bearing portion, it forms cantilever bearings by the described main shaft part that supports described axle; Cylinder body, it is arranged to be fixed on the special position in the described bearing portion, and forms columnar pressing chamber; Be inserted into can be in described pressing chamber to-and-fro motion and have the piston of pin-and-hole; Be inserted and secured on the wrist pin in the described pin-and-hole; And connecting rod, it is used to connect described eccentric axial portion and described piston, and at one end has big stomidium portion and have small end hole portion at the other end,
Satisfy formula (2) by first center line in the axle center that described piston is shown with angle a2 (rad) and the predetermined angle b2 (rad) that second center line that the axle center of described pin-and-hole is shown forms, and by be associated set angle b2 based on the gap between described bearing portion and the described main shaft part, described absolute value c2 (rad) with respect to the angle of inclination of described bearing portion.
a2＝π/2+b2(rad) (2)
10. hermetic type compressor as claimed in claim 9,
Wherein said angle b2 be set to described angle absolute value c2 more than 0.5 times to below 3.3 times.
11. hermetic type compressor as claimed in claim 9,
Wherein said angle b2 be set to described angle absolute value c2 more than 1.0 times to below 2.7 times.
12. hermetic type compressor as claimed in claim 9,
Wherein said angle b2 be set to described angle absolute value c2 below 2.5 times do not comprise 0 (rad) on the occasion of, described pressing chamber has and is formed the increasable tapered portion of a side internal diameter that makes a side direction that is positioned at upper dead center from described piston be positioned at lower dead centre, and the angle d2 that between the axle center of the axle center of described piston and described pressing chamber, forms during along described tapered portion slip when the periphery of described piston and the described angle b2 sum absolute value c2 that is set to described angle more than 0.3 times to below 4 times.
13. hermetic type compressor as claimed in claim 12,
Wherein said angle b2 and described angle d2 sum be set to described angle absolute value c2 more than 1.0 times to below 3.2 times.
14. hermetic type compressor as claimed in claim 13,
Wherein said angle d2 be set to described angle b2 more than 0.5 times to below 1.5 times.
15. hermetic type compressor as claimed in claim 9,
The straight portion that also has corresponding position, the upper end portion of the described pressing chamber side of described piston when being positioned at upper dead center, forms adjacent to described tapered portion with described piston.
16. hermetic type compressor as claimed in claim 9,
Wherein when described piston was positioned at lower dead centre, at least a portion of described piston was exposed from described cylinder body.
17. hermetic type compressor as claimed in claim 9,
Wherein in the vertical direction is formed asymmetrically described piston.
18. a hermetic type compressor comprises:
The compressing member that is contained in the motor-driven components in the seal container and drives by described motor-driven components,
Wherein, described compressing member comprises: axle, and it has the main shaft part by described motor-driven components rotation and driving, and is formed on an end of described main shaft part and the eccentric axial portion that described main shaft part is integrally moved; Bearing portion, it forms cantilever bearings by the described main shaft part that supports described axle; Cylinder body, it is arranged to be fixed on the special position in the described bearing portion, and forms columnar pressing chamber; Be inserted into can be in described pressing chamber to-and-fro motion and have the piston of pin-and-hole; Be inserted and secured on the wrist pin in the described pin-and-hole; And connecting rod, it is used to connect described eccentric axial portion and described wrist pin, and at one end has big stomidium portion and have small end hole portion at the other end,
By first center line in the axle center that described big stomidium portion is shown and illustrate angle a3 that second center line in the axle center of described small end hole portion forms be set to based on the axle gap between described bearing portion and the described main shaft part, described with respect to the absolute value c3 at the angle of inclination of described bearing portion more than 0.5 times to below 3.3 times.
19. hermetic type compressor as claimed in claim 18,
Wherein said angle a3 be set to described angle absolute value c3 more than 1.0 times to below 2.7 times.
20. hermetic type compressor as claimed in claim 18,
Wherein said angle b3 be set to described angle absolute value c3 below 2.5 times do not comprise 0 (rad) on the occasion of, described pressing chamber has and is formed the increasable tapered portion of a side internal diameter that makes a side direction that is positioned at upper dead center from described piston be positioned at lower dead centre, and the angle d3 that between the axle center of the axle center of described piston and described pressing chamber, forms during along described tapered portion slip when the periphery of described piston and the predetermined angle b3 sum absolute value c3 that is set to described angle more than 0.3 times to below 4 times.
21. hermetic type compressor as claimed in claim 20,
Wherein said angle b3 and described angle d3 sum be set to described angle absolute value c3 more than 1.0 times to below 3.2 times.
22. hermetic type compressor as claimed in claim 21,
Wherein said angle d3 be set to described angle b3 more than 0.5 times to below 1.5 times.
23. hermetic type compressor as claimed in claim 18,
The straight portion that also has corresponding position, the upper end portion of the described pressing chamber side of described piston when being positioned at upper dead center, forms adjacent to described tapered portion with described piston.
24. hermetic type compressor as claimed in claim 13,
Wherein when described piston was positioned at lower dead centre, at least a portion of described piston was exposed from described cylinder body.
25. hermetic type compressor as claimed in claim 13,
Wherein in the vertical direction is formed asymmetrically described connecting rod.
26. freezing and refrigerating equipment that is equipped with as any one the described hermetic type compressor in the claim 1 to 25.
CN2009801004632A 2008-05-12 2009-05-11 Closed type compressor and freezing apparatus using the same Active CN101802404B (en)

Applications Claiming Priority (9)

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JP2008124319 2008-05-12
JP2008-124319 2008-05-12
JP2008300493 2008-11-26
JP2008-300493 2008-11-26
JP2008306001 2008-12-01
JP2008-306001 2008-12-01
JP2008-307176 2008-12-02
JP2008307176 2008-12-02
PCT/JP2009/002036 WO2009139138A1 (en) 2008-05-12 2009-05-11 Closed type compressor and freezing apparatus using the same

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CN101802404B CN101802404B (en) 2012-08-29

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KR (1) KR101245024B1 (en)
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CN106062363A (en) * 2014-02-25 2016-10-26 松下知识产权经营株式会社 Sealed compressor and refrigeration device

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KR102461070B1 (en) * 2020-11-27 2022-11-01 엘지전자 주식회사 Hermetic compressor

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CN103615377A (en) * 2013-11-26 2014-03-05 武汉凌达压缩机有限公司 Reciprocating compressor
CN103615377B (en) * 2013-11-26 2016-05-18 武汉凌达压缩机有限公司 A kind of reciprocating compressor
CN106062363A (en) * 2014-02-25 2016-10-26 松下知识产权经营株式会社 Sealed compressor and refrigeration device

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JP5170111B2 (en) 2013-03-27
WO2009139138A1 (en) 2009-11-19
CN101802404B (en) 2012-08-29
KR20110003365A (en) 2011-01-11
JP2011508840A (en) 2011-03-17

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