Scroll compressor and refrigerating apparatus

Abstract

To suppress vibration of a scroll compressor causing leakage of a refrigerant.SOLUTION: A scroll compressor (90) includes: a scroll compression mechanism (40); a crankshaft (30); a main bearing (35); and a pin bearing (37). The scroll compression mechanism (40) has a fixed scroll (41) and a movable scroll (42). The crankshaft (30) has a main shaft section (31) and a pin section (32). The crankshaft (30) turns the movable scroll (42). The main bearing (35) has a first service life (T1). The main bearing (35) supports the main shaft section (31). The pin bearing (37) has a second service life (T0) longer than the first service life (T1). The pin bearing (37) supports the pin section (32).SELECTED DRAWING: Figure 4

Description

[Technical Field]

[0001] The present disclosure relates to a scroll compressor and a refrigeration device. [Background technology]

[0002] The scroll compressor disclosed in Patent Document 1 (Japanese Patent No. 7174287) is mounted on a refrigeration system. The scroll compressor has a scroll compression mechanism that compresses a refrigerant and a crankshaft that transmits power to the scroll compression mechanism. The crankshaft has a main shaft portion and pin portions that are eccentric from the main shaft portion. The compressor further has a main bearing that supports the main shaft portion and a pin bearing that supports the pin portions. Summary of the Invention [Problem to be solved by the invention]

[0003] When a refrigeration system uses a highly flammable refrigerant, refrigerant leakage can cause a serious accident. If the piping of a refrigeration system is damaged, the refrigerant can leak from the piping. The damage to the piping can be caused by vibration of the scroll compressor. Vibration of the scroll compressor can occur if there is a misalignment in the movement of the components of the scroll compression mechanism. Such a misalignment can occur, for example, due to damage to the pin bearing that supports the pin portion of the crankshaft. [Means for solving the problem]

[0004] A scroll compressor according to a first aspect includes a scroll compression mechanism, a crankshaft, a main bearing, and a pin bearing. The scroll compression mechanism has a fixed scroll and a movable scroll. The crankshaft has a main shaft portion and a pin portion. The crankshaft orbits the movable scroll. The main bearing has a first life. The main bearing supports the main shaft portion. The pin bearing has a second life longer than the first life. The pin bearing supports the pin portion.

[0005] With this configuration, the pin bearing has a longer lifespan than the main bearing. Therefore, the pin bearing has excellent durability, and in the event of a crankshaft abnormality, the main bearing is damaged first, allowing the crankshaft to be stopped by control or other means. Compared to a case in which the pin bearing is damaged first, causing a deviation in the orbiting motion of the movable scroll, which then causes vibration in the compressor and piping, this configuration further reduces the risk of piping damage and resulting refrigerant leakage.

[0006] A scroll compressor according to a second aspect is the scroll compressor according to the first aspect, wherein the pressure that the main bearing receives from the crankshaft is P1 (N / m 2 ), the peripheral speed of the crankshaft at the main bearing is V1 (m / s), and the pressure that the pin bearing receives from the crankshaft is P0 (N / m 2 ) and the peripheral speed of the crankshaft at the pin bearing is V0 (m / s),

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[0007] With this configuration, the pin bearing exhibits a smaller PV value, which is the product of pressure and peripheral velocity, than the main bearing. Therefore, it can be expected that the life of the pin bearing will be longer than that of the main bearing.

[0008] A scroll compressor according to a third aspect is the scroll compressor according to the first or second aspect, further comprising an auxiliary bearing. The auxiliary bearing is arranged on the opposite side of the main bearing from the pin bearing. The auxiliary bearing supports a main shaft portion. When the distance from the center height of the auxiliary bearing to the center height of the main bearing is L1 (m), the height dimension of the main bearing is H1 (m), the distance from the center height of the auxiliary bearing to the center height of the pin bearing is L0 (m), and the height dimension of the pin bearing is H0 (m),

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[0009] With this configuration, by carrying out a predetermined dimensional design, it is expected that the pin bearing will exhibit a smaller value for the product of pressure and peripheral velocity than the main bearing, thereby making it possible to extend the life of the pin bearing longer than the life of the main bearing.

[0010] A scroll compressor according to a fourth aspect is the scroll compressor according to the third aspect,

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[0011] With this configuration, the height dimension (H0) of the pin bearing is secured to be a large dimension of more than 0.7 times the height dimension (H1) of the main bearing, which is expected to result in a long life for the pin bearing.

[0012] A scroll compressor according to a fifth aspect is the scroll compressor according to the third aspect,

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[0013] With this configuration, the height dimension (H0) of the pin bearing is secured to be extremely large, more than 0.9 times the height dimension (H1) of the main bearing, and therefore the pin bearing can be reliably expected to have a long lifespan.

[0014] A scroll compressor according to a sixth aspect is a scroll compressor according to any one of the third to fifth aspects, wherein the distance (L1) from the center height of the auxiliary bearing to the center height of the main bearing is greater than 9 times and less than 11 times the height dimension (H1) of the main bearing.

[0015] This configuration ensures a sufficient gap between the main bearing and the auxiliary bearing, thereby suppressing tilt of the crankshaft.

[0016] A scroll compressor according to a seventh aspect is the scroll compressor according to any one of the first to sixth aspects, wherein the scroll compression mechanism compresses a highly flammable refrigerant.

[0017] According to this configuration, the compressor handles a highly flammable refrigerant. Therefore, since the highly flammable refrigerant is handled by a compressor that is less likely to generate vibrations, refrigerant leakage is suppressed and the risk of fire or the like is reduced.

[0018] A scroll compressor according to an eighth aspect is the scroll compressor according to the seventh aspect, wherein the highly flammable refrigerant is propane.

[0019] According to this configuration, the compressor uses propane. Therefore, since propane is handled by a compressor that is less likely to generate vibrations, refrigerant leakage is suppressed and the risk of fire and the like is reduced.

[0020] A scroll compressor according to a ninth aspect includes the scroll compressor according to any one of the first to eighth aspects.

[0021] According to this configuration, the refrigeration system includes a compressor that generates less vibration, and therefore vibration of the piping of the refrigeration system can be reduced. [Brief explanation of the drawings]

[0022] [Figure 1] 1 is a schematic diagram showing a refrigerant circuit of a refrigeration device 100. FIG. [Figure 2] FIG. 2 is a cross-sectional view of a scroll compressor 90. [Figure 3] FIG. 2 is an enlarged cross-sectional view of a scroll compressor 90. [Figure 4] FIG. 2 is a cross-sectional view of a scroll compressor 90. DETAILED DESCRIPTION OF THE INVENTION

[0023] <Embodiment> (1) Overall structure 1 shows a refrigerant circuit of a refrigeration device 100 according to this embodiment. The refrigeration device 100 provides cold heat or hot heat to a user. Specific embodiments of the refrigeration device 100 may include an air conditioner, a refrigerator, a freezer, a water heater, a floor heating device, and the like.

[0024] The refrigeration system 100 is configured as a refrigerant circuit that circulates refrigerant R. The refrigerant R is a highly flammable refrigerant, such as propane. The refrigeration system 100 has a heat source unit 110, a utilization unit 120, and a communication pipe group 130. The heat source unit 110 has a scroll compressor 90, a four-way switching valve 91, a heat source heat exchanger 92, a heat source fan 93, a heat source expansion valve 94, a liquid stop valve 95, a gas stop valve 96, and an accumulator 97. The utilization unit 120 has a utilization heat exchanger 98 and a utilization fan 99. The communication pipe group 130 has a liquid communication pipe 131 and a gas communication pipe 132.

[0025] The scroll compressor 90 compresses the refrigerant R in a low-pressure gas state to a high-pressure gas state. The four-way switching valve 91 realizes the connection shown by the solid lines in Fig. 1 when the refrigeration apparatus 100 performs cold heat supply operation, and realizes the connection shown by the dashed lines in Fig. 1 when the refrigeration apparatus 100 performs hot heat supply operation. When the refrigeration apparatus 100 performs cold heat supply operation, the heat source heat exchanger 92 functions as a condenser or a radiator, and the utilization heat exchanger 98 functions as an evaporator or a heat absorber. When the refrigeration apparatus 100 performs hot heat supply operation, the heat source heat exchanger 92 functions as an evaporator or a heat absorber, and the utilization heat exchanger 98 functions as a condenser or a radiator.

[0026] (2) Configuration of the scroll compressor 90 2 shows a cross section of a scroll compressor 90. The scroll compressor 90 has a casing 10, a motor 20, a crankshaft 30, a scroll compression mechanism 40, a partition member 50, and a support member 55.

[0027] (2-1) Casing 10 The casing 10 has a body portion 11, an upper portion 12, and a lower portion 13 that are hermetically welded together. An internal space S is formed within the casing 10. The internal space S accommodates a motor 20, a crankshaft 30, a scroll compression mechanism 40, a partition member 50, and a support member 55. Furthermore, the internal space S is filled with a refrigerant R. A suction pipe 15 is connected to the upper portion 12 for drawing in the refrigerant R in a low-pressure gas state. A discharge pipe 16 is connected to the body portion 11 for discharging the refrigerant R in a high-pressure gas state. An oil reservoir 14 is provided near the lower portion 13. The oil reservoir 14 stores lubricating oil L for lubricating the scroll compression mechanism 40.

[0028] (2-2) Motor 20 The motor 20 converts electrical energy into rotation of the crankshaft 30. The motor 20 includes a stator 21 and a rotor 22.

[0029] The stator 21 has a cylindrical shape and is fixed to the body 11. A plurality of coils (not shown) are provided in the stator 21. When a current flows through the coils, the coils generate a magnetic field.

[0030] The rotor 22 also has a cylindrical shape. The rotor 22 is rotatably disposed in a cavity in the center of the stator 21. A crankshaft 30 is fixed to the cavity of the rotor 22 itself. A permanent magnet (not shown) is attached to the rotor 22. The permanent magnet interacts with the magnetic field generated by the coil to generate a rotational force for the rotor 22.

[0031] (2-3) Crankshaft 30 The crankshaft 30 transmits the rotation of the rotor 22 to the scroll compression mechanism 40. The crankshaft 30 has a main shaft portion 31 that shares a rotation axis with the rotor 22, and a pin portion 32 that is eccentric from the main shaft portion 31. When the rotor 22 rotates, the main shaft portion 31 rotates in response, and the pin portion 32 revolves to describe a circular orbit.

[0032] The main shaft portion 31 is rotatably supported by a main bearing 35 and an auxiliary bearing 36. The pin portion 32 is rotatably supported by a pin bearing 37. The auxiliary bearing 36 is disposed on the opposite side of the main bearing 35 from the pin bearing 37.

[0033] An oil passage 33 is formed in the crankshaft 30. The oil passage 33 is used to draw up the lubricating oil L from the oil reservoir 14 and supply it to the scroll compression mechanism 40.

[0034] (2-4) Scroll compression mechanism 40 The scroll compression mechanism 40 compresses the low-pressure gaseous refrigerant R drawn in through the suction pipe 15 to a high-pressure gaseous state. The scroll compression mechanism 40 has a fixed scroll 41 and a movable scroll 42. Both the fixed scroll 41 and the movable scroll 42 have spiral scroll wraps. The scroll wraps of the fixed scroll 41 and the movable scroll 42 are arranged to mesh with each other, thereby forming multiple compression chambers 43. A pin bearing 37 is disposed in a boss portion 44 extending from the bottom of the movable scroll 42. A pin portion 32 is inserted into the pin bearing 37. When the pin portion 32 orbits, the movable scroll 42 orbits in response. This changes the volume of the multiple compression chambers 43, compressing the refrigerant R in the compression chambers 43.

[0035] (2-5) Partition member 50 The partition member 50 divides the internal space S. The scroll compression mechanism 40 is disposed above the partition member 50, and the motor 20 is disposed below the partition member 50. The partition member 50 has a first partition member 60 and a second partition member 70.

[0036] (2-6) Support member 55 The support member 55 is installed below the motor 20 and supports the lower part of the main shaft portion 31 of the crankshaft 30. The support member 55 is fixed to the body portion 11. The auxiliary bearing 36 is attached to the support member 55.

[0037] (3) Configuration of the partition member 50 FIG. 3 shows the periphery of the partition member 50 in the scroll compressor 90. The first partition member 60 is fixed to the body portion 11 by welding. The first partition member 60 has a center hole 61 and an elastic groove 62. The center hole 61 is for allowing the crankshaft 30 to pass through. The main bearing 35 is attached to the center hole 61. The elastic groove 62 has a circular ring shape with a first diameter D1. The elastic groove 62 is for absorbing vibrations and tilts of the crankshaft 30 by promoting elastic deformation of the first partition member 60.

[0038] The second partition member 70 is located above the first partition member 60 and supports the scroll compression mechanism 40. The second partition member 70 is provided with a center hole 71 and a seal ring groove 72. The center hole 61 is for allowing the crankshaft 30 to pass through. The seal ring groove 72 has a circular ring shape with a second diameter D2. A seal ring 77 is installed in the seal ring groove 72.

[0039] The second partition member 70 supports the fixed scroll 41 at its peripheral edge. A seal ring 77 provided on the second partition member 70 contacts the movable scroll 42 near the center hole 71 and supports the movable scroll 42. This contact causes the second partition member 70 to divide the internal space S into an upper space and a lower space. As the movable scroll 42 orbits, the movable scroll 42 and the seal ring 77 slide against each other at this contact point.

[0040] The first partition member 60 has a recess 65. On the other hand, the second partition member 70 has a protrusion 75 that protrudes downward. The first partition member 60 and the second partition member 70 are fixed to each other by press-fitting the protrusion 75 into the recess 65. Furthermore, the second partition member 70 is fixed to the body 11 of the casing 10 by press-fitting.

[0041] A storage space 51 is formed between the first partition member 60 and the second partition member 70. A portion of the lubricating oil L pumped up from the oil reservoir 14 is stored in the storage space 51. The lubricating oil L in the storage space 51 passes through an oil flow path 63 formed in the first partition member 60 and an oil flow path 73 formed in the second partition member 70, and is then supplied to the thrust surface 45 where the fixed scroll 41 and the movable scroll 42 are in contact with each other.

[0042] (4) Parts configuration (4-1) Dimensions 4 shows the dimensions of the components of the scroll compressor 90. The height dimension of the pin bearing 37 is H0 (m). The height dimension of the main bearing 35 is H1 (m). The distance from the auxiliary bearing 36 to the pin bearing 37 is L0 (m). The distance from the auxiliary bearing 36 to the main bearing 35 is L1 (m). Here, each distance is measured from the center height position of the main bearing 35, auxiliary bearing 36, and pin bearing 37.

[0043] The distance L1 from the center height of the auxiliary bearing to the center height of the main bearing is preferably set to be greater than 9 times the height dimension H1 of the main bearing and less than 11 times the height dimension H1 of the main bearing .

[0044] The following relationship holds among the force F0 (N) that pin bearing 37 receives from crankshaft 30, the force F1 (N) that main bearing 35 receives from crankshaft 30, the distance L0 (m) from auxiliary bearing 36 to pin bearing 37, and the distance L1 (m) from auxiliary bearing 36 to main bearing 35.

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[0045] This is because the moment acting on the pin bearing 37 and the moment acting on the main bearing 35 are balanced with the auxiliary bearing 36 as a fulcrum.

[0046] (4-2) Relationship between bearing lifespan The pin bearing 37 has durability represented by a lifespan T0. The main bearing 35 has durability represented by a lifespan T1. The main bearing 35 and the pin bearing 37 are designed so that the lifespan T0 of the pin bearing 37 is longer than the lifespan T1 of the main bearing 35. The relationship between the lifespans is expressed by the following formula.

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[0047] (4-3) PV value magnitude relationship The PV values ​​of the pin bearing 37 and the main bearing 35 are set to realize the magnitude relationship of [Equation 2] between the life T1 of the main bearing 35 and the life T0 of the pin bearing 37. The PV value means the product of the pressure received by the bearing and the circumferential speed of the crankshaft.

[0048] The scroll compressor 90 is designed so that the following relationship holds between α0 (N / (m·s)), which is the PV value of the pin bearing 37, and α1 (N / (m·s)), which is the PV value of the main bearing 35.

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[0049] The PV value of the pin bearing 37, α0 (N / (m·s)), is the pressure P0 (N / m 2 ) and the peripheral speed V0 (m / s) of the crankshaft 30 at the pin bearing 37, is defined by the following formula.

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[0050] The PV value of the main bearing 35, α1 (N / (m·s)), is the pressure P1 (N / m 2 ) and the peripheral speed V1 (m / s) of the crankshaft 30 at the main bearing 35, it is defined by the following formula.

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[0051] (4-4) Relationships between parameters The force that the bearing receives can be calculated from the pressure that the bearing receives.

[0052] The force F0 (N) that the pin bearing 37 receives from the crankshaft 30, the pressure P0 (N / m 2 ), the area of ​​the pin bearing 37 S0 (m 2 ) the following mathematical relationship holds:

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[0053] The force F1 (N) that the main bearing 35 receives from the crankshaft 30, the pressure P1 (N / m 2 ), the area of ​​the main bearing 35 S1 (m 2 ) the following mathematical relationship holds:

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[0054] The area of ​​the bearing can be calculated from the radius and height of the bearing.

[0055] Area of ​​pin bearing 37 S0 (m 2 ), the radius R0 (m) of the pin bearing 37, and the height dimension H0 (m) of the pin bearing 37, the following mathematical relationship is established.

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[0056] Area S1 of main bearing 35 (m 2 ), the radius R1 (m) of the main bearing 35, and the height dimension H1 (m) of the main bearing 35, the following mathematical relationship holds:

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[0057] The following mathematical relationship holds between the peripheral speed V0 (m / s) of the crankshaft 30 at the pin bearing 37, the radius R0 (m) of the pin bearing 37, and the angular speed ω (rad / s) of the crankshaft.

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[0058] The following mathematical relationship holds between the peripheral speed V1 (m / s) of the crankshaft 30 at the main bearing 35, the radius R1 (m) of the main bearing 35, and the angular speed ω (rad / s) of the crankshaft.

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[0059] (4-5) Bearing height relationship Below, the magnitude relationship of the PV values ​​shown in [Equation 3] is converted into the magnitude relationship of the bearing heights. By combining [Equation 3], [Equation 4], and [Equation 5], the following equation is obtained.

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[0060] Further integrating [Number 10] and [Figure 11] into this gives the following formula:

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[0061] Further integrating [Number 6] and [Figure 7] into this gives the following equation:

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[0062] If we further integrate [Equation 1] into this, we get the following equation.

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[0063] Further integrating [Number 8] and [Number 9] into this, we get the following equation.

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[0064] Now, consider the design shown in Figure 4. As mentioned above, the distance L0 (m) is measured starting from the center height of the pin bearing 37, and the distance L1 (m) is measured starting from the center height of the main bearing 35. Therefore, the distance L0 (m) from the auxiliary bearing 36 to the pin bearing 37 can be converted as follows:

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[0065] Therefore, from [Equation 16] and [Equation 17], the following equation is established.

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[0066] Here, if we express H0⇒x and H1⇒y, we obtain the following formula.

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[0067] If we solve this equation (19) for x, we get the following solution:

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[0068] As described above, it is preferable to set the distance L1 from the center height of the auxiliary bearing 36 to the center height of the main bearing 35 to be greater than 9 times and less than 11 times the height dimension H1 of the main bearing 35. Therefore, in [Equation 20], the reference value 1 is substituted for the height dimension H1 (i.e., y) of the main bearing 35, and 10, which is 10 times H1, is substituted for the distance L1 from the auxiliary bearing 36 to the main bearing 35. This results in the following numerical values:

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[0069] That is, if the height dimension H0 (i.e., x) of the pin bearing 37 is set to a dimension greater than approximately 0.9 times the height dimension H1 (i.e., y) of the main bearing 35, the magnitude relationship of the PV values ​​defined by [Equation 3] will be satisfied, and ultimately the magnitude relationship of the lifespans defined by [Equation 2] will be satisfied. In other words, it is desirable that the height dimension H0 of the pin bearing 37 and the height dimension H1 of the main bearing 35 satisfy the relationship defined by the following mathematical formula.

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[0070] It is not common in the actual design of scroll compressor 90 to ensure that height H0 of pin bearing 37 is as large as 0.9 times height H1 of main bearing 35. Therefore, a design that satisfies the following equation, which is a slight relaxation of [Equation 22], can also be considered.

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[0071] This design also makes it possible to extend the life T0 of pin bearing 37 longer than in a general design, and is expected to have the effect of suppressing refrigerant leakage.

[0072] (5) Features (5-1) The lifespan T0 of pin bearing 37 is longer than the lifespan T1 of main bearing 35. Therefore, pin bearing 37 has excellent durability, and in the event of an abnormality in crankshaft 30, main bearing 35 is damaged first, so that rotation of crankshaft 30 can be stopped by control or other means. Compared to a case in which pin bearing 37 is damaged first, causing a deviation in the orbiting motion of movable scroll 42 and resulting in vibration of scroll compressor 90 or piping, this configuration further reduces the risk of piping damage and resulting refrigerant leakage.

[0073] (5-2) With regard to the PV value, which is the product of pressure and peripheral velocity, the pin bearing 37 exhibits a smaller value than the main bearing 35. Therefore, it can be expected that the life T0 of the pin bearing 37 is longer than the life T1 of the main bearing 35.

[0074] (5-3) Because appropriate dimensional design is performed for the distance between the bearings and the height of the bearings, it is expected that the pin bearing 37 will exhibit a smaller PV value than the main bearing 35. Therefore, the life T0 of the pin bearing 37 can be made longer than the life T1 of the main bearing 35.

[0075] (5-4) The height H0 of the pin bearing 37 is secured to be a large dimension of more than 0.7 or 0.9 times the height H1 of the main bearing 35. Therefore, a long life T0 of the pin bearing 37 can be expected.

[0076] (5-5) A large distance L1 is ensured between the main bearing 35 and the auxiliary bearing 36. Therefore, tilting of the crankshaft 30 is suppressed.

[0077] (5-6) The refrigerant R is a highly flammable refrigerant such as propane. This highly flammable refrigerant is handled by the scroll compressor 90, which is less likely to generate vibration. Therefore, refrigerant leakage is suppressed, and the risk of serious accidents is reduced.

[0078] (6) Variations (6-1) Variation A In the above-described embodiment, refrigerant R is a highly flammable refrigerant such as propane. Alternatively, refrigerant R may be a refrigerant other than a highly flammable refrigerant.

[0079] (6-2) Variation B In the above-described embodiment, the partition member 50 is composed of the first partition member 60 and the second partition member 70. Alternatively, the partition member 50 may be composed of a single member.

[0080] <Conclusion> Although the embodiments of the present disclosure have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the present disclosure as defined in the claims. [Explanation of symbols]

[0081] 30: Crankshaft 31: Main shaft part 32: Pin section 35: Main bearing 36: Auxiliary bearing 37: Pin bearing 40:Scroll compression mechanism 41: Fixed scroll 42: Movable scroll 90:Scroll compressor 100: Refrigeration equipment F0: Force acting on the pin bearing from the crankshaft F1: Force acting on the main bearing from the crankshaft 30 H0: Height dimension of pin bearing H1: Height of main bearing L0: Distance from auxiliary bearing to pin bearing L1: Distance from auxiliary bearing to main bearing P0: Pressure applied to the pin bearing by the crankshaft P1: Pressure applied to the main bearing by the crankshaft R0: Radius of pin bearing R1: Radius of main bearing S0: Area of ​​pin bearing S1: Main bearing area T0: Pin bearing life (second life) T1: Main bearing life (first life) V0: Circumferential speed of the crankshaft in the pin bearing V1: Circumferential speed of the crankshaft at the main bearing ω: Angular velocity of the crankshaft [Prior art documents] [Patent documents]

[0082] [Patent Document 1] Patent No. 7174287

Claims

1. a scroll compression mechanism (40) having a fixed scroll (41) and a movable scroll (42); a crankshaft (30) having a main shaft portion (31) and a pin portion (32) for orbiting the movable scroll; First life (T １ ) and a main bearing (35) that supports the main shaft portion; A second life (T ０ ) and a pin bearing (37) for supporting the pin portion; A scroll compressor (90) comprising:

2. The pressure that the main bearing receives from the crankshaft is P １ (N / m ２ ), The peripheral speed of the crankshaft in the main bearing is V １ (m / s), The pressure received from the pin bearing by the crankshaft is P ０ (N / m ２ ), The peripheral speed of the crankshaft at the pin bearing is V ０ (m / s), When [0012] The relationship between The scroll compressor according to claim 1 .

3. an auxiliary bearing (36) arranged on the opposite side of the main bearing from the pin bearing and supporting the main shaft portion; Furthermore, The distance from the center height of the auxiliary bearing to the center height of the main bearing is L １ (m), The height dimension of the main bearing is H １ (m), The distance from the center height of the auxiliary bearing to the center height of the pin bearing is L ０ (m), The height dimension of the pin bearing is H ０ (m), When [0016] The relationship between The scroll compressor according to claim 1 . [Request Item 4] [Number 23] The relationship between The scroll compressor according to claim 3. 【Request Item 5】 【Number 22】 The relationship between The scroll compressor according to claim 3.

6. The distance (L １ ) is the height dimension (H １ ) is greater than 9 times and less than 11 times, The scroll compressor according to claim 4 or 5.

7. The scroll compression mechanism compresses a highly flammable refrigerant. The scroll compressor according to any one of claims 1 to 5.

8. The highly flammable refrigerant is propane. The scroll compressor according to claim 7.

9. The scroll compressor according to any one of claims 1 to 5, A refrigeration device (100) comprising:

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