Scroll compressors and refrigeration systems

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] This disclosure relates to a scroll compressor and a refrigeration system. [Background technology]

[0002] The scroll compressor disclosed in Patent Document 1 (Japanese Patent No. 7174287) is installed in a refrigeration system. The scroll compressor has a scroll compression mechanism for compressing a refrigerant and a crankshaft for transmitting power to the scroll compression mechanism. The crankshaft has a main shaft portion and a pin portion eccentric to 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 portion. [Overview of the Initiative] [Problems that the invention aims to solve]

[0003] When a refrigeration system handles highly flammable refrigerants, refrigerant leakage can cause serious accidents. Damage to the refrigeration system's piping can lead to refrigerant leakage. Piping damage can be caused by vibrations in the scroll compressor. Vibrations in the scroll compressor can occur if there is misalignment in the movement of components in the scroll compression mechanism. Such misalignments can result, for example, from damage to the pin bearings supporting the crankshaft pin. [Means for solving the problem]

[0004] A scroll compressor according to the first aspect comprises 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 rotates the movable scroll. The main bearing has a first lifespan. The main bearing supports the main shaft portion. The pin bearing has a second lifespan that is longer than the first lifespan. The pin bearing supports the pin portion.

[0005] In this configuration, the pin bearings have a longer lifespan than the main bearings. Therefore, the pin bearings have superior durability, and in the event of a crankshaft malfunction, the main bearings will fail first, allowing the crankshaft rotation to be stopped by control or other means. Compared to a case where the pin bearings fail first, causing misalignment of the movable scroll's orbital motion and resulting vibration of the compressor and piping, this configuration reduces the risk of piping damage and the resulting refrigerant leakage.

[0006] A scroll compressor relating to the second aspect is a scroll compressor relating to the first aspect, wherein the pressure received by the main bearing from the crankshaft is P1 (N / m 2 ), where V1 (m / s) is the peripheral speed of the crankshaft in the main bearing, and P0 (N / m) is the pressure exerted on the pin bearing by the crankshaft. 2 ), when the peripheral speed of the crankshaft in a pin bearing is V0 (m / s),

number

[0007] In this configuration, the pin bearing exhibits a smaller PV value (product of pressure and peripheral speed) than the main bearing. Therefore, the pin bearing can be expected to have a longer lifespan than the main bearing.

[0008] A scroll compressor relating to the third aspect is a scroll compressor relating to the first or second aspect, further comprising an auxiliary bearing. The auxiliary bearing is positioned on the opposite side of the main bearing from the pin bearing. The auxiliary bearing supports the main shaft. 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),

number

[0009] With this configuration, by designing the dimensions accordingly, it is expected that the pin bearing will exhibit a smaller value than the main bearing in terms of the product of pressure and peripheral speed. Therefore, the lifespan of the pin bearing can be extended beyond that of the main bearing.

[0010] A scroll compressor relating to the fourth perspective is a scroll compressor relating to the third perspective,

number

[0011] This configuration ensures that the height dimension (H0) of the pin bearing is more than 0.7 times the height dimension (H1) of the main bearing. Therefore, a long lifespan for the pin bearing can be expected.

[0012] A scroll compressor relating to the fifth perspective is a scroll compressor relating to the third perspective,

number

[0013] This configuration ensures that the height dimension (H0) of the pin bearing is extremely large, exceeding 0.9 times the height dimension (H1) of the main bearing. Therefore, a long lifespan for the pin bearing can be reliably expected.

[0014] A scroll compressor relating to the sixth viewpoint is a scroll compressor relating to any one of the third, fourth, or fifth viewpoints, 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. Consequently, the tilt of the crankshaft is suppressed.

[0016] A scroll compressor relating to the seventh viewpoint is a scroll compressor relating to any one of the sixth viewpoints from the first viewpoint, 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 unlikely to generate vibrations, refrigerant leakage is suppressed and risks such as ignition are reduced.

[0018] The scroll compressor according to the 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 handles propane. Therefore, since propane is handled by a compressor that is unlikely to generate vibrations, refrigerant leakage is suppressed and risks such as ignition are reduced.

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

[0021] According to this configuration, the refrigeration device includes a compressor with little vibration. Therefore, the vibration of the piping of the refrigeration device can be reduced.

Brief Description of the Drawings

[0022] [Figure 1] It is a schematic diagram showing the refrigerant circuit of the refrigeration device 100. [Figure 2] It is a cross-sectional view of the scroll compressor 90. [Figure 3] It is an enlarged view of the cross-section of the scroll compressor 90. [Figure 4] It is a cross-sectional view of the scroll compressor 90.

Embodiments for Carrying Out the Invention

[0023] <Embodiment> (1) Overall Configuration Figure 1 shows the refrigerant circuit of the refrigeration system 100 according to this embodiment. The refrigeration system 100 provides the user with cold heat or hot heat. Specific embodiments of the refrigeration system 100 may include air conditioning systems, refrigerators, freezers, water heaters, floor heating systems, etc.

[0024] The refrigeration system 100 is configured as a refrigerant circuit that circulates a refrigerant R. The refrigerant R is a highly flammable refrigerant, such as propane. The refrigeration system 100 includes a heat source unit 110, a utilization unit 120, and a group of connecting pipes 130. The heat source unit 110 includes 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 shut-off valve 95, a gas shut-off valve 96, and an accumulator 97. The utilization unit 120 includes a utilization heat exchanger 98 and a utilization fan 99. The group of connecting pipes 130 includes a liquid connecting pipe 131 and a gas connecting 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 line in Figure 1 when the refrigeration system 100 is performing cold supply operation, and the connection shown by the dashed line in Figure 1 when the refrigeration system 100 is performing heat supply operation. When the refrigeration system 100 is performing cold supply operation, the heat source heat exchanger 92 functions as a condenser or heat radiator, and the utilization heat exchanger 98 functions as an evaporator or heat absorber. When the refrigeration system 100 is performing heat supply operation, the heat source heat exchanger 92 functions as an evaporator or heat absorber, and the utilization heat exchanger 98 functions as a condenser or heat radiator.

[0026] (2) Configuration of the scroll compressor 90 Figure 2 shows a cross-section of the scroll compressor 90. The scroll compressor 90 includes 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 section 11, an upper section 12, and a lower section 13 that are airtightly welded to each other. An internal space S is formed inside the casing 10. The internal space S houses the motor 20, the crankshaft 30, the scroll compression mechanism 40, the partition member 50, and the support member 55. Furthermore, the internal space S is filled with refrigerant R. An intake pipe 15 for drawing in refrigerant R in a low-pressure gas state is connected to the upper section 12. A discharge pipe 16 for discharging refrigerant R in a high-pressure gas state is connected to the body section 11. An oil reservoir 14 is provided near the lower section 13. Lubricating oil L for lubricating the scroll compression mechanism 40 is stored in the oil reservoir 14.

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

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

[0030] The rotor 22 also has a cylindrical shape. The rotor 22 is positioned to rotate within the central cavity of the stator 21. The crankshaft 30 is fixed to the cavity within the rotor 22 itself. Permanent magnets (not shown) are attached to the rotor 22. The permanent magnets interact with the magnetic field generated by the coils to produce the rotational force of 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 to the main shaft portion 31. When the rotor 22 rotates, the main shaft portion 31 rotates in accordance with it, and the pin portion 32 pivots in 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 pivotally supported by a pin bearing 37. The auxiliary bearing 36 is positioned on the opposite side of the pin bearing 37 from the main bearing 35.

[0033] An oil passage 33 is formed inside the crankshaft 30. The oil passage 33 is for drawing lubricating oil L from the oil reservoir 14 and supplying 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 from the suction pipe 15 into 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 helical scroll wraps. The scroll wraps of the fixed scroll 41 and the movable scroll 42 are arranged to interlock with each other, thereby forming a plurality of compression chambers 43. A pin bearing 37 is located on a boss portion 44 extending from the lower part of the movable scroll 42. A pin portion 32 is inserted into the pin bearing 37. When the pin portion 32 rotates, the movable scroll 42 rotates in accordance with it. This changes the volume of the plurality of compression chambers 43, and the refrigerant R in the compression chambers 43 is compressed.

[0035] (2-5) Partition member 50 The partition member 50 divides the internal space S. A scroll compression mechanism 40 is located above the partition member 50, and a motor 20 is located below the partition member 50. The partition member 50 includes 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. An auxiliary bearing 36 is attached to the support member 55.

[0037] (3) Configuration of partition member 50 Figure 3 shows the area around the partition member 50 in the scroll compressor 90. The first partition member 60 is fixed to the body 11 by welding. The first partition member 60 is provided with a central hole 61 and an elastic groove 62. The central hole 61 is for the passage of the crankshaft 30. The main bearing 35 is mounted in the central hole 61. The elastic groove 62 has an annular shape with a first diameter D1. The elastic groove 62 is for absorbing vibrations and tilts of the crankshaft 30 by promoting the 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 central hole 71 and a seal ring groove 72. The central hole 61 is for the passage of the crankshaft 30. The seal ring groove 72 has an annular 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. Furthermore, a seal ring 77 provided on the second partition member 70 contacts the movable scroll 42 near the central hole 71, supporting the movable scroll 42. This contact divides the internal space S into an upper and lower space. Since the movable scroll 42 performs a rotational motion, 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 projects 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 portion 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 the oil passage 63 formed in the first partition member 60 and the oil passage 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.

[0042] (4) Components (4-1) Dimensions Figure 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] 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.

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

number

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

[0046] (4-2) Relationship between the lifespan of bearings The pin bearing 37 has a lifespan represented by T0. The main bearing 35 has a lifespan represented by 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.

number

[0047] (4-3) Relationship between PV values In order to achieve the relationship [Equation 2] between the lifespan T1 of the main bearing 35 and the lifespan T0 of the pin bearing 37, the PV values ​​of the pin bearing 37 and the main bearing 35 are set. The PV value is the product of the pressure exerted on the bearing and the peripheral speed of the crankshaft.

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

number

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

number

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

number

[0051] (4-4) Relationship between parameters The force received by the bearing can be calculated from the pressure received by the bearing.

[0052] The force F0 (N) received by the pin bearing 37 from the crankshaft 30, the pressure P0 (N / m 2 ), and the area S0 (m 2 ) of the pin bearing 37 satisfy the following mathematical relationship. [Equation]

[0053] The force F1 (N) received by the main bearing 35 from the crankshaft 30, the pressure P1 (N / m 2 ), and the area S1 (m 2 ) of the main bearing 35 satisfy the following mathematical relationship. [Equation]

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

[0055] The area S0 (m 2 ), radius R0 (m), and height dimension H0 (m) of the pin bearing 37 satisfy the following mathematical relationship. [Equation]

[0056] The area S1 (m 2 ), radius R1 (m), and height dimension H1 (m) of the main bearing 35 satisfy the following mathematical relationship. [Equation]

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

number

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

number

[0059] (4-5) Relationship between the heights of the bearings In the following, the relative sizes of the PV values ​​shown in [Equation 3] are converted to relative sizes of the bearing heights. Combining [Equation 3], [Equation 4], and [Equation 5] yields the following formula.

number

[0060] Integrating [Equation 10] and [Figure 11] into this further yields the following formula.

number

[0061] Integrating this further with [Equation 6] and [Figure 7] results in the following equation.

number

[0062] Integrating this with [Equation 1] results in the following equation.

number

[0063] If we further integrate [Equation 8] and [Equation 9] into this, we get the following equation.

number

[0064] Now, consider the design shown in Figure 4. As mentioned above, distance L0(m) is measured starting from the center height of the pin bearing 37, and 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.

number

[0065] Therefore, from [Equation 16] and [Equation 17], the following equation holds true.

number

[0066] If we represent H0 as x and H1 as y, we obtain the following equation.

number

[0067] Solving this [Equation 19] for x yields the following solution.

number

[0068] As mentioned 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], we substitute the reference value of 1 for the height dimension H1 (i.e., y) of the main bearing 35, and substitute 10, which is 10 times H1, for the distance L1 from the auxiliary bearing 36 to the main bearing 35. This yields the following values.

number

[0069] In other words, 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 relationship between the PV values ​​defined in [Equation 3] will be satisfied, and consequently, the relationship between the lifespans defined in [Equation 2] will be satisfied. To put it another way, 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 given by the following formula.

number

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

number

[0071] This design also allows for a longer lifespan T0 of the pin bearing 37 compared to typical designs, and is expected to have the effect of suppressing refrigerant leakage.

[0072] (5) Characteristics (5-1) The lifespan T0 of the pin bearing 37 is longer than the lifespan T1 of the main bearing 35. Therefore, the pin bearing 37 has superior durability, and in the event of a malfunction in the crankshaft 30, the main bearing 35 will be damaged first, allowing the rotation of the crankshaft 30 to be stopped by control or other means. Compared to the case where the pin bearing 37 is damaged first, causing a misalignment of the orbital motion of the movable scroll 42 and resulting in vibration of the scroll compressor 90 and piping, this configuration reduces the risk of piping damage and resulting refrigerant leakage.

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

[0074] (5-3) Since the distance between bearings and the height of the bearings have been appropriately designed, it is expected that the pin bearing 37 will have 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 dimension H0 of the pin bearing 37 is set to be larger than 0.7 or 0.9 times the height dimension H1 of the main bearing 35. Therefore, a long lifespan T0 of the pin bearing 37 can be expected.

[0076] (5-5) The distance L1 between the main bearing 35 and the auxiliary bearing 36 is large. Therefore, the tilt 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 a scroll compressor 90, which is less prone to generating vibrations. Therefore, refrigerant leakage is suppressed, and the risk of serious accidents is reduced.

[0078] (6) Variant (6-1) Variation A In the embodiment described above, the refrigerant R is a highly flammable refrigerant such as propane. Alternatively, the 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 a first partition member 60 and a second partition member 70. Alternatively, the partition member 50 may be composed of a single member.

[0080] <Conclusion> While embodiments of this disclosure have been described above, it should be understood that various modifications to the form and details are possible without departing from the spirit and scope of this disclosure as described in the claims. [Explanation of Symbols]

[0081] 30: Crankshaft 31: Main shaft part 32: Pin part 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 exerted by the crankshaft on the pin bearing F1: Force exerted by the crankshaft 30 on the main bearing H0: Height dimension of pin bearing H1: Height dimension of the main bearing L0: Distance from auxiliary bearing to pin bearing L1: Distance from auxiliary bearing to main bearing P0: Pressure exerted by the crankshaft on the pin bearing P1: Pressure exerted on the main bearing by the crankshaft R0: Radius of the pin bearing R1: Radius of the main bearing S0: Area of ​​pin bearing S1: Area of ​​the main bearing T0: Pin bearing life (second life) T1: Main bearing life (first life) V0: Peripheral speed of the crankshaft in a pin bearing V1: Peripheral speed of the crankshaft in 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) that rotates the movable scroll, First life (T １ ) and a main bearing (35) that supports the main shaft portion, A second life (T) that is longer than the first life. ０ ) and a pin bearing (37) that supports the pin portion, A scroll compressor (90) equipped with the following:

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 that the pin bearing receives from the crankshaft is P ０ (N / m ２ ), The peripheral speed of the crankshaft in the pin bearing is V ０ (m / s) In that case, [Math 12] The relationship holds true. The scroll compressor according to claim 1.

3. An auxiliary bearing (36) is positioned on the opposite side of the pin bearing from the main bearing and supports the main shaft portion. Furthermore, Let the distance from the center height of the auxiliary bearing to the center height of the main bearing be 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 aforementioned pin bearing is H ０ (m), In that case, [Number 16] The relationship holds true. The scroll compressor according to claim 1. [Request Item 4] [Number 23] The relationship holds true. The scroll compressor according to claim 3. 【Request Item 5】 【Number 22】 The relationship holds true. The scroll compressor according to claim 3.

6. The distance (L) from the center height of the auxiliary bearing to the center height of the main bearing １ ) is the height dimension (H) of the main bearing. １ ) is greater than 9 times and less than 11 times. A scroll compressor according to claim 4 or claim 5.

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

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

9. A scroll compressor according to any one of claims 1 to 5, A refrigeration device (100) equipped with the following.

Images