JP5334662B2 - Compressor - Google Patents

Description

  The present invention relates to a hermetic compressor, and more particularly to a compressor with improved safety.

  As a countermeasure when an abnormally high pressure is generated in the compressor, a high-pressure cut protection device is generally provided on the refrigerant discharge side to stop the compressor. However, when a malfunction or failure occurs in the high-pressure cut protection device, the abnormal high pressure of the compressor cannot be detected by another device, and abnormal high-pressure refrigerant and refrigeration oil are discharged from the compressor and compressed. It is assumed that the possibility of damaging the refrigerant piping or the like in the middle of the refrigerant discharge flow path other than the machine increases. If it does so, since the refrigerant | coolant and refrigerating machine oil of an abnormal high pressure state will leak into external space, danger will increase. In addition, the compressor shell cannot withstand abnormally high pressure, and there is a risk of damage to the shell, such as cracks.

An apparatus provided with a safety device that eliminates such a risk has been proposed. As such, “In an air conditioner that cools air using the latent heat of vaporization of carbon dioxide CO ₂ refrigerant, when the air conditioner is subjected to an action such as an abnormal pressure increase or repeated pressure change, There has been proposed an “air conditioner equipped with a safety device that breaks or ruptures a fragile portion that prevents scattering of fragments and the like provided in the air conditioner” (see, for example, Patent Document 1). This safety device is configured by providing a weak part such as a thin part in a part of a metal pipe.

JP 2000-130896 A (page 4, FIG. 2)

  The safety device described in Patent Document 1 is provided in a refrigerant pipe that connects each device of an air conditioner. And damage is made small by breaking or rupturing a weak part. However, if the refrigerant pipe is broken or ruptured, the pieces of the refrigerant pipe are scattered, and the danger is not completely eliminated. Further, by providing the film, scattering of fragments of the refrigerant pipe can be reduced, but it can be assumed that the film is damaged by the fragments or the high-pressure refrigerant. Furthermore, it is necessary to consider that the refrigerant leaks.

  In addition, the safety device as described in Patent Document 1 does not assume aging of each device of the air conditioner. In particular, it is known that a compressor, which is a component device of an air conditioner, significantly changes with time when used for many years. That is, when the compressor is used for many years, metal fatigue or wear inside the compressor occurs, and the frequency of failure of the compressor increases. Therefore, it is necessary to design not only the safety measures against the compressor abnormality but also the safety measures due to the aging of the compressor.

  The present invention has been made in order to solve the above-described problems, and an object of the present invention is to provide a compressor that closes a fail at the time of abnormally high pressure or aging of the compressor inside the compressor.

A compressor according to the present invention is housed in a sealed container and compresses a sucked refrigerant; a drive mechanism that is housed in the sealed container and drives the compression mechanism; and the sealed container A suction side pipe connected to the high pressure side refrigerant chamber, a high pressure side refrigerant chamber that partitions the high pressure refrigerant and the low pressure refrigerant compressed by the compression mechanism, and the high pressure side refrigerant chamber that passes through the sealed container. , and a discharge side pipe for discharging the refrigerant gas high pressure outside the sealed container, the inside of the discharge side pipe of the sealed container, the vulnerable parts against the outside of the discharge side pipe of the sealed vessel vulnerable And the fragile portion is destroyed before the discharge-side pipe in which the fragile portion is not formed .

  According to the compressor according to the present invention, the failure of the compressor due to abnormal high pressure or aging of the compressor or failure such as failure is closed inside the compressor by destroying the fragile part first, so safety is improved. It can be significantly improved.

2 is a longitudinal sectional view showing an example of a sectional configuration of the compressor according to Embodiment 1. FIG. It is explanatory drawing for demonstrating the weak part formed in discharge side piping. 4 is a longitudinal sectional view showing an example of a sectional configuration of a compressor according to Embodiment 2. FIG. It is explanatory drawing for demonstrating the strength calculation method of piping wall thickness. It is a SN diagram which shows the relationship between the stress amplitude (S) of a metal material, and a repetition number (N). It is an expanded section schematic diagram expanding and showing typically X portion.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1.
FIG. 1 is a longitudinal sectional view showing an example of a sectional configuration of a compressor 100 according to Embodiment 1 of the present invention. The configuration and operation of the compressor 100 will be described with reference to FIG. The compressor 100 is shown as an example of a hermetic scroll compressor. For example, a refrigerator or a freezer, a vending machine, an air conditioner, a refrigeration apparatus, a water heater, or the like of a refrigeration cycle (heat pump cycle). It is a component. In addition, in the following drawings including FIG. 1, the relationship of the size of each component may be different from the actual one.

  The compressor 100 sucks the refrigerant circulating in the refrigeration cycle, compresses it, and discharges it as a high-temperature and high-pressure state. The compressor 100 can be classified into a compression mechanism unit 16 and a drive mechanism unit 17. The compression mechanism portion 16 and the drive mechanism portion 17 are accommodated in a sealed container (shell) 10. The sealed container 10 is a pressure container. As shown in FIG. 1, the compression mechanism unit 16 is disposed on the upper side of the sealed container 10, and the drive mechanism unit 17 is disposed on the lower side of the sealed container 10. The bottom of the hermetic container 10 is a sump 11 for storing the refrigerating machine oil 1. In addition, the closed container 10 is connected to a suction side pipe 12 for sucking refrigerant gas and a discharge side pipe 13 for discharging refrigerant gas. A portion of the discharge side pipe 13 inside the sealed container 10 is thinned to form a fragile portion 90 (described in detail in FIG. 2).

  The compression mechanism unit 16 has a function of compressing the refrigerant gas sucked from the suction side pipe 12 and discharging it to the discharge space 15 in the sealed container 10. The discharge space 15 is formed in an upper space inside the compressor 100 and is a high-pressure space. The refrigerant gas discharged to the discharge space 15 is discharged to the outside of the compressor 100 from the discharge side pipe 13 communicating with the discharge space 15. Here, the high-pressure chamber forming member 15a is installed in the upper space inside the sealed container 10 so as to form the discharge space 15 serving as the high-pressure chamber. The high-pressure chamber forming member 15 a is configured to seal a predetermined amount of high-pressure refrigerant discharged from the discharge port 63. That is, the high-pressure chamber forming member 15a partitions the high-pressure refrigerant compressed by the compression mechanism 16 and the low-pressure refrigerant, and the discharge space 15 acts as a high-pressure side refrigerant chamber.

  The compression mechanism unit 16 is roughly configured by a turning scroll 50, a fixed scroll 60, and a frame 70. As shown in FIG. 1, the orbiting scroll 50 is arranged on the lower side, and the fixed scroll 60 is arranged on the upper side. The fixed scroll 60 is formed with a wrap portion 62 which is a spiral protrusion standing on one surface. Further, the orbiting scroll 50 is also formed with a wrap portion 52 which is a spiral protrusion standing on one surface. The orbiting scroll 50 and the fixed scroll 60 are mounted in the sealed container 10 with the wrap portion 52 and the wrap portion 62 engaged with each other. And between the lap | wrap part 52 and the lap | wrap part 62, the compression chamber 18 from which a volume changes relatively is formed.

  The fixed scroll 60 is fixed to the frame 70 by bolts or the like (not shown). A discharge port 63 that discharges the compressed and high-pressure refrigerant gas is formed at the center of the fixed scroll 60. Then, the compressed and high pressure refrigerant gas is discharged into the discharge space 15 provided in the upper part of the fixed scroll 60. The orbiting scroll 50 performs a revolving orbiting movement without rotating about the fixed scroll 60. In addition, a hollow cylindrical orbiting scroll boss portion 53 is formed substantially at the center of the surface of the orbiting scroll 50 opposite to the surface on which the lap portion 52 is formed (hereinafter referred to as a thrust surface 55). An eccentric pin portion 41 provided at an upper end of a crankshaft 40 described later is fitted (engaged) with the orbiting scroll boss portion 53.

  The frame 70 is fixed to the inner peripheral surface of the hermetic container 10, and a through hole is formed in the center portion for allowing the crankshaft 40 to pass through. Further, the frame 70 is formed with an oil drain hole 71 penetrating from the thrust surface 55 side of the orbiting scroll 50 to the lower side in the axial direction so that the refrigerating machine oil 1 lubricating the thrust surface 55 is returned to the sump 11. It has become. Although FIG. 1 shows an example in which only one oil drain hole 71 is formed, the present invention is not limited to this. For example, two or more oil drain holes 71 may be formed. The frame 70 may be fixed to the inner peripheral surface of the sealed container 10 by shrink fitting or welding.

  The drive mechanism unit 17 serves to drive the orbiting scroll 50 of the compression mechanism unit 16. That is, when the drive mechanism unit 17 drives the orbiting scroll 50 via the crankshaft 40, the compression mechanism unit 16 compresses the refrigerant gas. The drive mechanism unit 17 includes a rotor 19 fixed to the crankshaft 40, a stator 20 housed in the hermetic container 10 and fixedly held, and a crankshaft 40 as a drive shaft. The rotor 19 is fixed to the crankshaft 40 and is driven to rotate when the energization of the stator 20 is started to rotate the crankshaft 40. Further, the outer peripheral surface of the stator 20 is fixedly supported by the sealed container 10 by shrink fitting or the like. That is, the rotor 19 and the stator 20 constitute a motor.

  The crankshaft 40 may be configured by selecting a material that has rigidity capable of securing an allowable deflection amount against an acting gas load, has good machinability, and can reduce costs. An upper end portion of the crankshaft 40 is formed with an eccentric pin portion 41 that is rotatably fitted to the orbiting scroll boss portion 53 of the orbiting scroll 50. An oil supply passage 42 communicating with the upper end surface is formed in the crankshaft 40. The oil supply passage 42 is a passage for the refrigerating machine oil 1 stored in the sump 11. The refrigerating machine oil 1 accumulated in the sump 11 sucks up the refrigerating machine oil 1 as the crankshaft 40 rotates, flows through the oil supply passage 42, and is supplied to the compression mechanism unit 16.

  An Oldham ring 80 is disposed between the orbiting scroll 50 and the fixed scroll 60 to prevent the rotation of the orbiting scroll 50 during the eccentric orbiting motion. The Oldham ring 80 is disposed between the orbiting scroll 50 and the fixed scroll 60, and serves to prevent the rotating motion of the orbiting scroll 50 and to enable a revolving motion. That is, the Oldham ring 80 functions as a rotation prevention mechanism for the orbiting scroll 50.

Here, the operation of the compressor 100 will be briefly described.
The rotor 19 constituting the motor rotates by receiving a rotational force from a rotating magnetic field generated by the stator 20. Accordingly, the crankshaft 40 fixed to the rotor 19 is driven to rotate. The orbiting scroll 50 is engaged with the eccentric pin portion 41 of the crankshaft 40, and the rotation rotation motion of the orbiting scroll 50 is converted into the revolution rotation motion by the rotation preventing mechanism of the Oldham ring 80. As the crankshaft 40 is driven to rotate, the refrigerant gas in the sealed container 10 flows into the compression chamber 18 formed by the wrap portion 62 of the fixed scroll 60 and the wrap portion 52 of the orbiting scroll 50, and the suction process starts.

  When the refrigerant gas is sucked into the compression chamber 18, the revolving orbiting motion of the eccentric orbiting scroll 50 shifts to a compression process for reducing the volume of the compression chamber 18. That is, in the compression mechanism section 16, when the orbiting scroll 50 makes a revolving orbiting motion, the refrigerant gas is taken in from the outermost peripheral openings of the orbiting scroll 50 and the wrap section 62 of the fixed scroll 60, which serve as suction ports. As the scroll 50 rotates, it gradually goes to the center while being compressed. The low-pressure refrigerant that has circulated through the refrigeration cycle flows into the sealed container 10 from the suction side pipe 12.

  Then, the refrigerant gas compressed in the compression chamber 18 moves to the discharge process. That is, the refrigerant gas passes through the discharge port 63 of the fixed scroll 60 and is discharged to the outside of the compressor 100 after passing through the discharge space 15. The refrigerant discharged from the discharge side pipe 13 of the compressor 100 is in a high temperature and high pressure state and flows into the condenser constituting the refrigeration cycle. Thereafter, when the energization of the stator 20 is stopped, the compressor 100 stops.

  FIG. 2 is an explanatory diagram for explaining the fragile portion 90 formed in the discharge side pipe 13. Based on FIG. 2, the weak part 90 is demonstrated in detail. Moreover, Fig.2 (a) is a cross-sectional schematic diagram which shows typically the cross-sectional structure of the compressor 100, FIG.2 (b) is an enlarged view which expands and shows the X part shown to Fig.2 (a) typically. It is a cross-sectional schematic diagram. Here, an example is shown in which a fragile portion 90 is formed in a part of the discharge side pipe 13 so as to have a pressure resistance equal to or lower than a predetermined pressure for the discharge side pipe 13.

  As shown in FIG. 2A, the inside of the sealed container 10 communicating with the suction side pipe 12 is a low pressure space (hereinafter referred to as a low pressure chamber 96), and the refrigerant discharged from the compression mechanism section 16 is discharged. The inside of the closed container 10 that conducts is a high-pressure space. As shown in FIGS. 1 and 2, the compressor 100 according to Embodiment 1 is provided with a high-pressure chamber forming member 15 a to form a discharge space 15 that becomes a high-pressure chamber, and the discharge-side piping 13 is connected to the high-pressure chamber forming member. The refrigerant in a high-pressure state is discharged by being inserted into 15 a and communicating with the discharge space 15.

  When the high pressure state in the compressor 100 rises abnormally, the refrigerant and the refrigerating machine oil 1 in an abnormally high temperature state are discharged, and equipment other than the refrigerant pipe or the compressor 100 (for example, a heat exchanger or an expansion valve) is destroyed. There is a possibility that.

Therefore, in the compressor 100 according to the first embodiment, the fragile portion 90 is provided in the discharge side pipe 13 so as to be prepared for an abnormality or failure of the compressor 100. The fragile portion 90 is configured by thinning a part of the discharge side pipe 13 in the compressor 100 into a ring shape so as to be equal to or lower than a pressure resistance predetermined for the discharge side pipe 13. Specifically, as shown in FIG. 2B, the thickness t ₂ of the thinned portion is made thinner than the overall thickness t ₁ of the discharge side pipe 13. When the pressure P is applied to the inside of the discharge pipe 13, when the stress generated in the portion other than the fragile part of the discharge side pipe 13 is σ ₀ , it is simply expressed as σ ₀ = (D ₁ × P) / 2t _1. it can. Here, D ₁ indicates the pipe outer diameter of the t ₁ portion.

Normally, the discharge side pipe 13 is designed to satisfy σ ₁ ≧ 4 × σ ₀ when the safety factor is about 4 times, that is, when the allowable tensile strength of the discharge side pipe 13 other than the fragile portion is σ ₁ . . Therefore, by making the thickness t ₂ of the fragile portion 90 thinner than t ₁ , the fragile portion 90 is destroyed first. For example, the allowable tensile strength of the fragile portion of the discharge side pipe 13 is σ _2, and the pipe thickness may be set so that σ ₁ ≧ 2 × σ ₂ . As described above, since the discharge side pipe 13 has a margin of four times the normal discharge pressure, the internal fragile portion 90 has a margin of twice the normal discharge output. Will not burst. On the other hand, when an abnormal pressure increase occurs, the stress generated in the internal fragile portion 90 is doubled or more, so that the internal fragile portion 90 is surely destroyed regardless of variations in material strength and processing accuracy. Since the high pressure portion and the low pressure portion communicate with each other inside the compressor 100 and the high pressure gas flows to the low pressure portion, an abnormal increase in high pressure can be prevented.

  Thus, if the weak part 90 is formed in the discharge side piping 13, even if abnormally high pressure occurs in the compressor 100, the weak part 90 will be destroyed first, and the pipe fragments will be compressed into the compressor 100. So that the refrigerant does not leak to the outside of the compressor 100. That is, a failure at an abnormally high pressure of the compressor 100 can be closed inside the compressor 100. In addition, even if the compressor 100 has been used for many years, the internal components of the compressor 100 have deteriorated over time, and the compressor 100 has failed, the failure at the time of failure of the compressor 100 can be closed inside the compressor 100. Therefore, it becomes an effective means as a safety measure.

In the first embodiment, the case where the fragile portion 90 is configured by thinning a part of the discharge side pipe 13 in the compressor 100 is described as an example. It is good also as the weak part 90 by setting one part material strength smaller than the material strength of the other part of the discharge side piping 13. FIG. Further, the case where the fragile portion 90 is configured by thinning a part of the discharge side pipe 13 inside the compressor 100 in a ring shape has been described as an example, but the present invention is not limited to this, and the discharge side inside the compressor 100 The fragile portion 90 may be configured by thinning a part of the pipe 13 in a fragmentary manner. As a supplement, the allowable tensile strength of the material used for the external pipe (the discharge side pipe 13 outside the sealed container 10) is σ _out , the stress generated by the external pipe when the internal pressure is applied is σ ₁ , and the internal pipe (the inside of the sealed container 10 It is usually designed so that σ _out / σ ₁ ≧ 4 as described above, where σ _in is the allowable tensile strength of the material used for the discharge side pipe 13) and σ ₂ is the stress generated in the internal pipe when the internal pressure is applied. Therefore, it is preferable to design so that σ _in / σ ₂ ≦ (σ _out / σ ₁ ) / 2.

  Furthermore, the weak pressure portion 90 is not a part of the discharge side pipe 13 but a part of the high pressure chamber forming member 15a forming the discharge space 15 serving as a high pressure chamber is determined in advance in the high pressure chamber forming member 15a. It is good also as a weak part as follows. In this case, by thinning a part of the high-pressure chamber forming member 15a or setting the material strength of a part of the high-pressure chamber forming member 15a to be smaller than the material strength of the other parts of the high-pressure chamber forming member 15a. What is necessary is just a weak part. Moreover, the thickness setting in the case of thinning is the same as that in the case of thinning a part of the discharge side pipe 13.

Here, the pipe thickness strength calculation method will be described in more detail. FIG. 4 is an explanatory diagram for explaining a pipe wall strength calculation method. FIG. 5 is a SN diagram showing the relationship between the stress amplitude (S) of metal material and the number of repetitions (N). FIG. 6 is an enlarged schematic cross-sectional view schematically showing an X portion in an enlarged manner. In FIG. 4, t ₀ represents the pipe wall thickness, D ₀ represents the pipe outer diameter, and P represents the pipe internal pressure. Further, σ ₀ represents the generated stress. In FIG. 5, the horizontal axis indicates the number of repetitions (N) of the metal material, and the vertical axis indicates the stress amplitude (S) of the metal material.

When pressure P is generated inside a pipe having a uniform thickness, the stress generated in the pipe can be generally expressed as t ₀ = (P × D ₀ ) / 2σ ₀ . When selecting the thickness of the pipe used for the pressure vessel 10 (thickness of the discharge side pipe 13), it is general to follow the refrigeration security rule related example criteria. In the destructive test according to this example standard, the criterion for acceptance is that the sample does not break at a destructive pressure less than four times the design pressure. For this reason, a pipe wall thickness that satisfies t ₀ ≧ 4 × (P × D ₀ ) / 2σy is usually selected. In other words, it can be said that the selected wall thickness has a margin of about four times the generated stress.

On the other hand, in an environment where it is used for many years, the internal pressure P acting on the discharge side pipe 13 greatly fluctuates and a repeated stress is generated. Therefore, the piping material considering the fatigue strength of the material of the discharge side pipe 13 is considered. Selection is required. In the calculation formula of the minimum thickness of the “pipe that receives pressure on the inner surface” in the refrigeration security rule example, it is expressed as t = (P × D ₀ ) / (2ση + 0.8P). Here, t represents the minimum thickness of the pipe, P represents the design pressure, D ₀ represents the outer diameter of the pipe, σ represents the allowable tensile stress of the material, and η represents the efficiency of the welded joint.

When a seamless pipe is used for the discharge side pipe 13, η = 1, and t = (P × D ₀ ) / (2σ + 0.8P) ≈ (P × D ₀ ) / 2σ. Also, in the example of the reference table related to the frozen safety rules, the minimum tensile strength σy and the allowable tensile stress σ of the stretched material such as copper and aluminum and the steel material such as carbon steel and alloy steel are σ≈σy / 4. Therefore, the above formula for calculating the minimum thickness can be replaced with t≈4 × (P × D ₀ ) / 2σy. That is, when considering the fatigue strength, the thickness selection is the same as described above.

  From the above, since the thickness setting in the pipe thickness selection (here, the discharge side pipe 13) of the pressure vessel (here, the sealed vessel 10) is about four times the minimum tensile strength, the thickness is less than that. If the thin portion (here, the fragile portion 90) is provided, the thin portion can be damaged first even if the piping is damaged due to insufficient strength of the piping. Moreover, when a thin part cannot be provided in a high voltage | pressure piping, the effect similar to the case where a thin part is provided in piping can be acquired by providing a thin part in the high pressure chamber formation member 15a.

  However, in an actual machine, the material strength and the processing dimensions always vary, so depending on the ratio of the design wall thickness to the wall thickness of the thin wall portion, it may be assumed that the thin wall portion will not be damaged first. Therefore, it is necessary to set the thickness of the thin portion in consideration of variations.

  The variation in the high cycle fatigue strength of the metal material is supposed to follow a normal distribution from past literatures and fatigue tests, and the standard deviation σ, which is an index of variation in the SN diagram shown in FIG. Generally, it is 7% to 10%. The ratio of the fatigue limit of the variation lower limit product to the fatigue limit σb of the variation center product due to normal distribution is approximately 0.67 to 0.53 even if σ = 7% to 10% and the probability of occurrence is 1 million. is there.

In view of the above, considering the variation in the fatigue limit of the metal material, in order to first break the thin wall portion provided in the pipe, the relationship between the pipe wall thickness and the thin wall thickness in FIG. _It can be considered that ₁ ≧ 2 × t ₂ may be set.

Further, even when the fragile portion 90 is made of materials having different material strengths, t × σ≈4 × (P × D ₀ ) is established as described above. In FIG. 6, in order to break the fragile portion 90 provided in the discharge side pipe 13 _first , the thickness t _{1 of the} pipe constituted by the material strength σ ₁ and the material strength in consideration of the fatigue strength described above. the relationship between the thickness t ₂ of that has been weakened portion 90 composed of sigma _2, believed to _{t 1 × σ 1 ≧ 2 ×} t 2 × may be set to about ₂ sigma.

For example, suppose that the material on the thickness t ₁ side is iron, the thickness is 5 mm, and the material on the thickness t ₂ side is copper. If the tensile strength of iron σ ₁ = 400 MPa and the tensile strength of copper σ ₂ = 200 MPa, the thickness of t ₂ is 5 × 400 ≧ 2 × t ₂ × 200, that is, 5 ≧ t ₂ from the above equation. Therefore, it may be set to 5 mm or less.

Embodiment 2. FIG.
FIG. 3 is a longitudinal sectional view showing an example of a sectional configuration of the compressor 100a according to Embodiment 2 of the present invention. Based on FIG. 3, the weak part 90a which is the characteristic part of Embodiment 2 is demonstrated in detail. This compressor 100a shows a case where it is a closed scroll compressor as in the compressor 100 according to Embodiment 1, for example, a refrigerator, a freezer, a vending machine, an air conditioner, a refrigeration apparatus, and the like. It is a constituent element of a refrigeration cycle such as a water heater. In the second embodiment, differences from the first embodiment will be mainly described, and the same parts as those in the first embodiment will be denoted by the same reference numerals and description thereof will be omitted.

  In the compressor 100a according to the second embodiment, the configuration of the fragile portion 90a is different from the configuration of the fragile portion 90 of the compressor 100 according to the first embodiment. The fragile portion 90a is formed in the gap 91 formed between the discharge side pipe 13 and the high pressure chamber forming member 15a by thinning the end of the discharge side pipe 13, and the discharge space 15 serving as the high pressure chamber. And a sealing material 92 that seals the differential pressure between the low pressure chamber 96 and the low pressure chamber 96. The sealing material 92 is made of a material that is destroyed when the pressure in the discharge space 15 becomes a predetermined pressure or higher. In addition, although the case where the gap 91 is configured by thinning the end of the discharge side pipe 13 has been described as an example, the high pressure chamber forming member 15a may be thinned instead of the discharge side pipe 13.

  Thus, if the weak part 90a is formed in the compressor 100a, even if an abnormal high pressure occurs in the compressor 100a, the weak part 90a (specifically, the sealing material 92) is first destroyed or deformed. As a result, the discharge side pipe 13 can be prevented from bursting, and the refrigerant does not leak to the outside of the compressor 100a. That is, the failure at the abnormally high pressure of the compressor 100a can be closed inside the compressor 100a. In addition, even if the compressor 100a has been used for many years, the internal parts of the compressor 100a have deteriorated over time, and the compressor 100a has failed, the failure at the time of failure of the compressor 100a can be closed inside the compressor 100a. Therefore, it becomes an effective means as a safety measure.

  DESCRIPTION OF SYMBOLS 1 Refrigerating machine oil, 10 airtight container, 12 suction side piping, 13 discharge side piping, 15 discharge space, 15a high pressure chamber formation member, 16 compression mechanism part, 17 drive mechanism part, 18 compression chamber, 19 rotor, 20 stator, 40 Crankshaft, 41 Eccentric pin part, 42 Oil supply flow path, 50 Orbiting scroll, 52 Lapping part, 53 Orbiting scroll boss part, 55 Thrust surface, 60 Fixed scroll, 62 Lapping part, 63 Discharge port, 70 Frame, 71 Oil drain hole , 80 Oldham ring, 90 weak part, 90a weak part, 91 gap, 92 sealing material, 96 low pressure chamber, 100 compressor, 100a compressor.

Claims (5)

A compression mechanism that is housed in a sealed container and compresses the sucked refrigerant;
A drive mechanism that is housed in the sealed container and drives the compression mechanism;
A suction side pipe connected to the sealed container;
A high-pressure side refrigerant chamber that partitions a high-pressure refrigerant compressed by the compression mechanism section and a low-pressure refrigerant;
A discharge side pipe that passes through the sealed container and is connected to the high pressure side refrigerant chamber and discharges the high pressure refrigerant gas out of the sealed container;
In the discharge side piping inside the sealed container, forming a fragile portion that becomes a fragile portion with respect to the discharge side piping outside the sealed container ,
The compressor characterized in that the fragile portion is broken before the discharge-side piping in which the fragile portion is not formed . 2. The compression according to claim 1, wherein the fragile portion is formed by making a wall thickness of a discharge side pipe inside the sealed container thinner than a thickness of a discharge side pipe outside the sealed container. Machine. The vulnerable part is
It forms by setting the thickness of the discharge side piping inside the said airtight container to less than 1/2 with respect to the wall thickness of the discharge side piping outside the said airtight container. Compressor. 2. The compression according to claim 1, wherein a material strength of a discharge- side pipe inside the sealed container is set as the fragile portion using a material weaker than a material strength of a discharge- side pipe outside the sealed container. Machine. 5. The compression according to claim 4, wherein the tensile strength of the discharge- side piping material inside the sealed container is made of a material that is less than half of the tensile strength of the discharge- side piping material outside the sealed container. Machine.

Images