Scroll compressor and refrigerating device

Abstract

A scroll compressor (90) is provided with 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 part (31) and a pin part (32). The crankshaft (30) rotates the movable scroll (42). The main bearing (35) has a first service life (T1). The main bearing (35) supports the main shaft part (31). The pin bearing (37) has a second service life (T0) that is longer than the first service life (T1). The pin bearing (37) supports the pin part (32).

Description

Scroll compressor and refrigeration device

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

[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 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.

[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.

[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 P １ (N / m ２ ), the peripheral speed of the crankshaft at the main bearing is V １ (m / s), and the pressure that the pin bearing receives from the crankshaft is P ０ (N / m ２ ), the peripheral speed of the crankshaft at the pin bearing is V ０ (m / s), The following relationship is established.

[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, and therefore the life of the pin bearing can be expected to be longer than the life 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 disposed on the opposite side of the main bearing from the pin bearing. The auxiliary bearing supports the main shaft portion. The distance from the center height of the auxiliary bearing to the center height of the main bearing is defined as 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 The following relationship is established.

[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, The following relationship is established.

[0011] According to this configuration, the height dimension (H ０ ) and the height dimension of the main bearing (H １ ) is secured. Therefore, a long life of the pin bearing can be expected.

[0012] A scroll compressor according to a fifth aspect is the scroll compressor according to the third aspect, The following relationship is established.

[0013] According to this configuration, the height dimension (H ０ ) and the height dimension of the main bearing (H １ ) is secured. Therefore, a long life of the pin bearing can be reliably expected.

[0014] A scroll compressor according to a sixth aspect is the scroll compressor according to any one of the third aspect to the fifth aspect, wherein the distance (L １ ) is the height dimension of the main bearing (H １ ) is more than 9 times and less than 11 times.

[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.

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

[0023] <Embodiment> (1) Overall Configuration Fig. 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 aspects 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 piping 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 shut-off valve 95, a gas shut-off valve 96, and an accumulator 97. The utilization unit 120 has a utilization heat exchanger 98 and a utilization fan 99. The communication piping group 130 has a liquid communication piping 131 and a gas communication piping 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 Figure 1 when the refrigeration system 100 performs cold heat supply operation, and realizes the connection shown by the dashed lines in Figure 1 when the refrigeration system 100 performs hot heat supply operation. When the refrigeration system 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 system 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 Scroll Compressor 90 Fig. 2 shows a cross section of the 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 refrigerant R. A suction pipe 15 is connected to the upper portion 12 for drawing in refrigerant R in a low-pressure gas state. A discharge pipe 16 is connected to the body portion 11 for discharging refrigerant R in a high-pressure gas state. An oil reservoir 14 is provided near the lower portion 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 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 at 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 refrigerant R, which is in a low-pressure gas state and is drawn in through the suction pipe 15, to a high-pressure gas 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 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 an annular shape with a first diameter D1. The elastic groove 62 promotes elastic deformation of the first partition member 60 to absorb vibrations and tilts of the crankshaft 30.

[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 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. 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) Configuration of 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 H ０ The height of the main bearing 35 is H １ The distance from the auxiliary bearing 36 to the pin bearing 37 is L ０ The distance from the auxiliary bearing 36 to the main bearing 35 is L １ Here, each distance is measured from the center height position of the main bearing 35, the auxiliary bearing 36, and the pin bearing 37.

[0043] Distance L from the center height of the auxiliary bearing 36 to the center height of the main bearing 35 １ is the height dimension H of the main bearing 35 １ It is preferable to set the value to be greater than 9 times and less than 11 times.

[0044] The force F acting on the pin bearing 37 from the crankshaft 30 ０ (N), the force F acting on the main bearing 35 from the crankshaft 30 １ (N), distance L from the auxiliary bearing 36 to the pin bearing 37 ０ (m), distance L from the auxiliary bearing 36 to the main bearing 35 １ The following relationship holds between (m):

[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 a lifespan of T ０ The main bearing 35 has a durability expressed as a life T １The pin bearing 37 has a durability expressed as follows: ０ is the life T of the main bearing 35 １ The main bearing 35 and the pin bearing 37 are designed so that the life span is longer than . The relationship between the life spans is expressed by the following formula.

[0047] (4-3) Relationship between PV values ​​and life T of main bearing 35 １ and the life T of the pin bearing 37 ０ The PV values ​​of the pin bearing 37 and the main bearing 35 are set in order to realize the magnitude relationship of [Equation 2] that holds between them. The PV value means the product of the pressure that the bearing receives and the circumferential velocity of the crankshaft.

[0048] The PV value of the pin bearing 37, α (N / (m·s)), and the PV value of the main bearing 35, α １ The scroll compressor 90 is designed so that the following relationship holds between the flow rate (N / (m·s)) and the pressure (N / (m·s)):

[0049] α, which is the PV value of the pin bearing 37 ０ (N / (m·s)) is the pressure P that the pin bearing 37 receives from the crankshaft 30 ０ (N / m ２ ) and the peripheral speed V of the crankshaft 30 at the pin bearing 37 ０ It is defined by the following formula using (m / s):

[0050] α, which is the PV value of the main bearing 35 １ (N / (m·s)) is the pressure P that the main bearing 35 receives from the crankshaft 30 １ (N / m ２ ) and the peripheral speed V of the crankshaft 30 at the main bearing 35 １ It is defined by the following formula using (m / s):

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

[0052] The force F acting on the pin bearing 37 from the crankshaft 30 ０ (N), pressure P that the pin bearing 37 receives from the crankshaft 30 ０ (N / m２ ), the area S of the pin bearing 37 ０ (m ２ ) the following mathematical relationship holds:

[0053] The force F acting on the main bearing 35 from the crankshaft 30 １ (N), pressure P that the main bearing 35 receives from the crankshaft 30 １ (N / m ２ ), the area S of the main bearing 35 １ (m ２ ) the following mathematical relationship holds: The area of ​​the bearing can be calculated from the radius and height of the bearing.

[0054] Area S of pin bearing 37 ０ (m ２ ), the radius R of the pin bearing 37 ０ (m), height dimension H of the pin bearing 37 ０ The following mathematical relationship holds between (m):

[0055] Area S of the main bearing 35 １ (m ２ ), radius R of main bearing 35 １ (m), the height dimension H of the main bearing 35 １ The following mathematical relationship holds between (m):

[0056] Circumferential speed V of the crankshaft 30 at the pin bearing 37 ０ (m / s), radius R of pin bearing 37 ０ The following mathematical relationship holds between the rotational speed (m) and the angular velocity ω (rad / s) of the crankshaft:

[0057] The peripheral speed V of the crankshaft 30 at the main bearing 35 １ (m / s), radius R of main bearing 35 １ The following mathematical relationship holds between the rotational speed (m) and the angular velocity ω (rad / s) of the crankshaft:

[0058] (4-5) Relationship between the heights of bearings Below, the relationship between the PV values ​​shown in [Equation 3] is converted to the relationship between the heights of bearings. By combining [Equation 3], [Equation 4], and [Equation 5], the following equation is obtained.

[0059] Further combining this with [Equation 10] and [FIG. 11], the following equation is obtained.

[0060] Further combining this with [Equation 6] and [Fig. 7], the following equation is obtained.

[0061] Further integrating this with [Equation 1] gives the following equation:

[0062] Further combining [Equation 8] and [Equation 9] into this, the following equation is obtained.

[0063] Now consider the design shown in Figure 4. As mentioned above, the distance L ０ (m) is measured from the center height of the pin bearing 37, and the distance L １ (m) is measured starting from the center height of the main bearing 35. Therefore, the distance L from the auxiliary bearing 36 to the pin bearing 37 ０ (m) can be transformed as follows:

[0064] Therefore, from [Equation 16] and [Equation 17], the following equation is established.

[0065] Here, H ０ ⇒x, H １ ⇒If we express it as y, we get the following formula.

[0066] When this [Equation 19] is solved for x, the following solution is obtained.

[0067] As described above, the distance L from the center height of the auxiliary bearing 36 to the center height of the main bearing 35 １ is the height dimension H of the main bearing 35 １ Therefore, in [Equation 20], the height dimension H of the main bearing 35 is preferably set to be greater than 9 times and smaller than 11 times.１ (i.e., y) is assigned a reference value of 1, and the distance L from the auxiliary bearing 36 to the main bearing 35 is calculated. １ H １ Substitute 10, which is 10 times the value of . This gives us the following values:

[0068] That is, the height dimension H of the pin bearing 37 ０ (i.e., x) is the height dimension H of the main bearing 35 １ (i.e., by setting the dimension to be larger than approximately 0.9 times y), the magnitude relationship of the PV value defined by [Equation 3] is satisfied, and furthermore, the magnitude relationship of the life defined by [Equation 2] is satisfied. ０ and the height dimension H of the main bearing 35 １ It is desirable that the relationship of the following formula be satisfied.

[0069] Height dimension H of pin bearing 37 ０ , the height dimension H of the main bearing 35 １ Securing a large value such as 0.9 times is not very common in the actual design of the scroll compressor 90. Therefore, a design that satisfies the following equation, which is a slight relaxation of [Equation 22], may be considered.

[0070] Even with this design, the life T ０ This allows the length to be longer than in conventional designs, which is expected to have the effect of suppressing refrigerant leakage.

[0071] (5) Features (5-1) Life T of the main bearing 35 １ The life T of the pin bearing 37 is ０ Therefore, the durability of pin bearing 37 is excellent, 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.

[0072] (5-2) Regarding 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, the life T ０ is the life T of the main bearing 35 １ You can expect it to be longer.

[0073] (5-3) Since the distance between the bearings and the height of the bearings are appropriately designed, it is expected that the pin bearing 37 will exhibit a smaller PV value than the main bearing 35. Therefore, the life T ０ is the life T of the main bearing 35. １ Can be made longer.

[0074] (5-4) Height dimension H of pin bearing 37 ０ , the height dimension H of the main bearing 35 １ Therefore, the pin bearing 37 has a long life T ０ can be expected.

[0075] (5-5) Distance L between the main bearing 35 and the auxiliary bearing 36 １ Therefore, the tilt of the crankshaft 30 is suppressed.

[0076] (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. This prevents refrigerant leakage and reduces the risk of serious accidents.

[0077] (6) Modifications (6-1) Modification A In the above-described embodiment, 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.

[0078] (6-2) Modification 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.

[0079] <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.

[0080] 30: Crankshaft 31: Main shaft portion 32: Pin portion 35: Main bearing 36: Auxiliary bearing 37: Pin bearing 40: Scroll compression mechanism 41: Fixed scroll 42: Orbiting scroll 90: Scroll compressor 100: Refrigeration device F ０ :Force acting on the pin bearing from the crankshaft F １ : Force acting on the main bearing from the crankshaft 30 H ０ : Height dimension of pin bearing H １ : Main bearing height L ０ : Distance from auxiliary bearing to pin bearing L １ : Distance from auxiliary bearing to main bearing P ０ : Pressure exerted on the pin bearing by the crankshaft P １ : Pressure that the main bearing receives from the crankshaft R ０ : Radius of pin bearing R １ : Radius of main bearing S ０ : Area of ​​pin bearing S １ : Area of ​​main bearing T ０ : Pin bearing life (second life) T １ : Main bearing life (first life) V ０ : circumferential speed of crankshaft at pin bearing V １ : circumferential speed of the crankshaft at the main bearing ω : angular speed of the crankshaft

[0081] 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) and rotating the movable scroll; and a first life (T １ a main bearing (35) that supports the main shaft portion and has a second life (T ０ a pin bearing (37) for supporting the pin portion.

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 at the pin bearing is V ０ (m / s), The scroll compressor according to claim 1 , wherein the following relationship holds:

3. An auxiliary bearing (36) is arranged on the opposite side of the pin bearing with respect to the main bearing and supports the main shaft portion, and 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 The scroll compressor according to claim 1 or 2, wherein the following relationship holds:

4. The scroll compressor according to claim 3 , wherein the following relationship holds:

5. The scroll compressor according to claim 3 , wherein the following relationship holds:

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 １ 6. The scroll compressor according to claim 3, wherein the ratio of the rotational speed of the scroll compressor to the rotational speed of the scroll is greater than 9 times and less than 11 times the rotational speed of the scroll compressor.

7. The scroll compressor according to any one of claims 1 to 6, wherein the scroll compression mechanism compresses a highly flammable refrigerant.

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

9. A refrigeration system (100) comprising a scroll compressor according to any one of claims 1 to 8.

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