SCROLL COMPRESSOR

Abstract

Scroll compressor comprising: a casing (1); a motor (2) for generating a driving force in the casing (1); a rotating shaft (3) which is rotated by the motor (2); a circulating spiral (42) which rotates around the rotating shaft (3); a fixed spiral (41) which, together with the circulating spiral (42), forms a compression chamber; a first bearing (71) which rotatably supports the rotating shaft (3) relative to the casing (1) on one side of the rotating shaft (3) with respect to the motor (2); a second bearing (72) which rotatably supports the rotating shaft (3) relative to the casing (1) on the other side of the rotating shaft (3) with respect to the motor (2);a third bearing (73) rotatably supports the rotating shaft (3) relative to the rotating spiral (42) on the opposite side of the first bearing (71) with respect to the second bearing (71), wherein: assuming that the center of the first bearing (71) is a first bearing center (CB1), the center of the second bearing (72) is a second bearing center (CB2), the center of the third bearing (73) is a third bearing center (CB3), and the center of a rotor (22) of the motor (2) is a motor center (CM) in an extension direction of the rotating shaft (3), a distance between the motor center (CM) and the third bearing center (CB3) (D12) is longer than a distance between the motor center (CM) and the first bearing center (CB1) (D11); and the distance between the second bearing center (CB2) and the motor center (CM) (D121) is longer than the distance between the second bearing center (CB2) and the third bearing center (CB3) (D122).

Description

TECHNICAL AREA

[0001] The present disclosure relates to a scroll compressor, and in particular a scroll compressor comprising a fixed spiral and a rotating spiral which revolves around the fixed spiral, while together with the fixed spiral defining a compression chamber, and thus enabling the compression of a refrigerant. STATE OF THE ART

[0002] Generally, a vehicle is equipped with an air conditioning system to cool / heat its interior. This air conditioning system includes a compressor, which is a component of a cooling system and compresses a low-temperature, low-pressure gaseous refrigerant, introduced from an evaporator, into a high-temperature, high-pressure gaseous refrigerant before supplying it to a condenser.

[0003] The compressor applied to a vehicle is normally configured as a mechanical compressor driven by the driving force transmitted by a motor, while the compressor applied to an electric vehicle, for example, is also configured as an electric compressor driven by the driving force transmitted by a motor.

[0004] Meanwhile, as an example of a compressor, there is a piston compressor, which compresses a refrigerant by means of reciprocating pistons, and a rotary compressor, which compresses a refrigerant while rotating. The piston compressor includes a crank compressor, which transmits a driving force from a power source to a set of pistons using a crank; a swashplate compressor, which transmits a driving force from a power source to a rotating shaft fitted with a swashplate compressor; and so on, depending on the method of power transmission from the power source. The rotary compressor includes a vane rotary compressor, which uses a rotating shaft and vanes; and a scroll compressor, which uses a rotating spiral and a fixed spiral.

[0005] The scroll compressor has been widely used for compressing a refrigerant in air conditioning systems or similar applications, as the scroll compressor has the advantage of being able to achieve a relatively higher compression ratio and a more stable torque by performing the intake, compression and discharge stroke of the refrigerant smoothly compared to other compressors.

[0006] Korean patent application No. 10-2016-0081675 discloses a conventional scroll compressor that is electrically driven.

[0007] With reference to Fig. In Korean patent application no. 10-2016-0081675, the scroll compressor includes a motor. 3 , which provides a driving force in a shell 11 generated, a rotating shaft 4 , which is powered by the engine 3 when rotated, a circumferential spiral 6 , which the rotating shaft 4 surrounds, and a fixed spiral 5, which together with the surrounding spiral 6 a compression chamber is defined.

[0008] The conventional scroll compressor includes a first bearing. 82 , that the rotating shaft 4 relative to the shell 11 on one side of the rotating shaft 4 regarding the engine 3 rotatably mounted, and a second bearing 81 , that the rotating shaft 4 relative to the case 11 on the other side of the rotating shaft 4 regarding the engine 3 rotatably mounted, and a third bearing 83 , that the rotating shaft 4 the circumferential spiral 6 on the opposite side of the first camp 82 regarding the second camp 81 It is mounted on a rotating bearing.

[0009] The conventional scroll compressor is problematic insofar as the second bearing 81 quickly becomes damaged and the operation of the scroll compressor stops.

[0010] In the event that the second camp 81 as a bearing with a higher load-bearing capacity than the first and third bearings 82 and 83 is configured to prevent the operation of the scroll compressor from being interrupted due to damage to the second bearing. 81 If it stops, the problem is that the cost, size and weight of the scroll compactor increase. Disclosure technical problem

[0011] Accordingly, one objective of the present disclosure is to provide a scroll compressor capable of preventing damage to a bearing that supports a rotating shaft between a motor and a rotating spiral.

[0012] Additionally, another objective of the present disclosure is to provide a scroll compactor that is able to avoid an increase in cost, size and weight due to a bearing. TECHNICAL SOLUTION

[0013] To solve the above problems according to one aspect of the present disclosure, a scroll compressor comprises a casing, a motor to generate a driving force in the casing, a rotating shaft which is turned by the motor, a circulating spiral which revolves around the rotating shaft, a fixed spiral which, together with the circulating spiral, defines a compression chamber, a first bearing which rotatably supports the rotating shaft relative to the casing on one side of the rotating shaft with respect to the motor, a second bearing which rotatably supports the rotating shaft relative to the casing on the other side of the rotating shaft with respect to the motor, and a third bearing which rotatably supports the rotating shaft relative to the circulating spiral on the opposite side of the first bearing with respect to the second bearing, assuming that the center of the first bearing is a first bearing center, and the center of the second bearing is a second bearing center.the center of the third bearing is a third bearing center, and the center of a rotor of the motor is a motor center in an extension direction of the rotating shaft, a distance between the first bearing center and the third bearing center is a predetermined distance, a distance between the motor center and the third bearing center is longer than a distance between the motor center and the first bearing center, and a distance between the second bearing center and the motor center is longer than a distance between the second bearing center and the third bearing center.

[0014] The distance between the engine center and the third bearing center can be 1.9 times greater than the distance between the engine center and the first bearing center.

[0015] The distance between the second bearing center and the engine center can be 1.17 to 1.22 times greater than the distance between the engine center and the first bearing center.

[0016] The distance between the second bearing center and the motor center can be 1.22 times greater than the distance between the motor center and the first bearing center.

[0017] The second bearing can have the same load-bearing capacity as at least one of the first and second bearings.

[0018] According to another aspect of the present disclosure, a scroll compressor includes a casing, a motor to generate a driving force in the casing, a rotating shaft rotated by the motor, a circulating spiral that rotates around the rotating shaft, a fixed spiral that, together with the circulating spiral, defines a compression chamber, a first bearing rotatably supporting the rotating shaft relative to the casing on one side of the rotating shaft with respect to the motor, a second bearing rotatably supporting the rotating shaft relative to the casing on the other side of the rotating shaft with respect to the motor, and a third bearing rotatably supporting the rotating shaft relative to the circulating spiral on the opposite side of the first bearing with respect to the second bearing, assuming that the center of the first bearing is a first bearing center and the center of the second bearing is a second bearing center.The center of the third bearing is a third bearing center in an extension direction of the rotating shaft, and the distance between the second bearing center and the third bearing center is shorter than the distance between the second bearing center and the first bearing center.

[0019] The distance between the second bearing center and the first bearing center can be in a range of 2.97 to 3.27 times greater than the distance between the second bearing center and the third bearing center.

[0020] Assuming that the center of a rotor of the motor is a motor center, the distance between the second bearing center and the third bearing center can be shorter than a distance between the second bearing center and the motor center.

[0021] The distance between the second bearing center and the engine center can be 1.60 to 1.80 times greater than the distance between the second bearing center and the third bearing center.

[0022] The distance between the engine center and the third bearing center can be longer than the distance between the engine center and the first bearing center.

[0023] The distance between the engine center and the third bearing center can be 1.9 times greater than the distance between the engine center and the first bearing center.

[0024] The distance between the first bearing center and the third bearing center can be a predetermined distance.

[0025] According to another aspect of the present disclosure, a scroll compressor includes a casing, a motor to generate a driving force in the casing, a rotating shaft which is turned by the motor, a circulating spiral which rotates around the rotating shaft, a fixed spiral which, together with the circulating spiral, defines a compression chamber, and a second bearing which rotatably supports the rotating shaft between the motor and the compression chamber, wherein the rotating shaft includes an eccentric bushing which rotates in an axial direction of the rotating shaft at a position overlapping with a second bearing, and the second bearing being located as close as possible to the compression chamber in a region where it does not interfere with the eccentric bushing.

[0026] According to another aspect of the present disclosure, a scroll compressor comprises a casing, a motor to generate a driving force in the casing, a rotating shaft which is turned by the motor, a circulating spiral which rotates around the rotating shaft, and a fixed spiral which, together with the circulating spiral, defines a compression chamber, wherein the casing includes a first partition to separate a space for receiving the motor from a space for receiving an inverter for controlling the motor, and a second partition to separate the space for receiving the motor from a second space for providing a compression chamber, wherein the first partition is formed with a first retaining groove in which a first bearing is inserted to support one end of the rotating shaft, and wherein the second partition is formed with a second retaining groove in which a second bearing is inserted to support the other end of the rotating shaft.and wherein the second retaining groove is formed by a surface of the second partition, 113 , which faces the compression chamber, is recessed.

[0027] The second bearing can be formed as low as possible within an area where it does not protrude in an axial direction from the second support groove. ADVANTAGEOUS EFFECTS

[0028] A scroll compressor according to the present disclosure comprises a first bearing rotatably supporting a rotating shaft relative to a shell on one side of the rotating shaft with respect to a motor, a second bearing rotatably supporting a rotating shaft relative to a shell on the other side of the rotating shaft with respect to a motor, and a third bearing rotatably supporting a rotating shaft relative to a circulating spiral on the opposite side of the rotating shaft with respect to the second bearing, wherein the distance between a first bearing center and a third bearing center can be a predetermined distance, the distance between a motor center and the third bearing center can be longer than the distance between the motor center and the first bearing center, and the distance between a second bearing center and the motor center can be longer than the distance between the second bearing center and the third bearing center.This makes it possible to avoid damage to the second bearing due to poor load conditions.

[0029] Additionally, the second bearing can have the same load-bearing capacity as at least one of the first and second bearings. This makes it possible to avoid an increase in cost, size, and weight due to the bearing. List of characters Fig. Figure 1 is a cross-sectional view representing a scroll compactor according to one embodiment of the present disclosure; Fig. 2 is a graphic representing loads in the scroll compressor according to the distance between a motor center and a first bearing center and the distance between the motor center and a third bearing center. Fig. 1. Applied to a first and third camp, and; Fig. Figure 3 is a graphic representing a load that, according to the distance between a second bearing center and the motor center and the distance between the motor center and the third bearing center in the scroll compressor, Fig. 1 is applied to a second warehouse. BEST WAY OF EXECUTION FOR THE INVENTION

[0030] A scroll compressor according to exemplary embodiments of the present disclosure is described in detail below with reference to the attached drawings.

[0031] Fig. Figure 1 is a cross-sectional view representing a scroll compressor according to an embodiment of the present disclosure; Fig. 2 is a graphic representing loads in the scroll compressor according to the distance between a motor center and a first bearing center and the distance between the motor center and a third bearing center. Fig. 1 can be applied to a first and third camp. Fig. Figure 3 is a graphic representing a load that, according to the distance between a second bearing center and the motor center and the distance between the motor center and the third bearing center in the scroll compressor of Fig. 1 is applied to a second warehouse.

[0032] With reference to Fig. 1 to Fig. 3. According to the embodiment of the present disclosure, the scroll compressor can have a casing 1 , an engine 2 , which provides a driving force in the shell 1 generated, a rotating shaft 3 , which is powered by the engine 2 is rotated, and a compression mechanism 4 , which is from the rotating shaft 3 is driven to compress a refrigerant.

[0033] The case 1 can a first case 11 include the engine 2 which includes a second housing 12 , which is an inverter 5to control the motor 2 records, and a third housing 13 , which the compression mechanism 4 records.

[0034] The first case 11 can a ring-shaped wall 111 , a first partition wall 112 , which is one end of the ring-shaped wall 111 covers, and a second partition 113 , which is the other end of the partition 111 covers, include. The ring-shaped wall 111 and the first and second partition wall 112 and 113 can define an engine mounting space in which the engine 2 has been recorded.

[0035] The second case 12 can be attached to the first partition wall 112 be coupled to define an inverter mounting space in which the inverter 5 has been recorded.

[0036] The first partition wall 112can separate the motor mounting compartment from the inverter mounting compartment and can create a connecting hole 1121 exhibiting that is formed on one side of it, so that a connector 6 , which the inverter 5 with the engine 2 connects, through the connecting hole 1211 proceeds.

[0037] The third case 113 can be attached to the second partition wall 113 be coupled to define a compression space in which the compression mechanism 4 has been recorded.

[0038] The second partition wall 113 It can separate the engine mounting chamber from the compression chamber and serve as the main frame supporting the compression mechanism. 4 holds. The second partition wall 113 can a storage hole 1131 exhibiting the one formed in the middle of it, so that the rotating shaft 3 for the motor's working connection 2 and the compression mechanism 4through the storage hole 1131 proceeds.

[0039] In the present embodiment, the compression mechanism can 4 a fixed spiral 41 include, which will be described later, the one on the second partition wall 113 is attached, and the third case 13 can be attached to the fixed spiral 41 to be attached. However, the present disclosure is not limited to this, and the third casing 13 can also be attached to the second partition wall 113 be attached while it is the compression mechanism 4 records.

[0040] The engine 2 can a stator 21 include the one in the first case 11 is attached, and a rotor 22 , which through interaction with the strator 21 in the stator 21 is being filmed.

[0041] The rotating shaft 3 can pass through the center of the rotor 22proceed, so that an end 31 the rotating shaft 3 towards the first partition wall 112 from the rotor 22 protrudes and the other end 32 from there towards the second partition wall 113 from the rotor 33 stands out.

[0042] The rotating shaft 3 can at one end 31 of which through a first camp 71 , which is in the middle of the first partition wall 112 It is provided and must be rotatably mounted.

[0043] The first partition wall 112 can a first holding groove 1122 exhibiting which is formed in the middle of it, so that the first bearing 71 and an end 31 the rotating shaft 3 into the first holding groove 1122 are inserted. The first camp 71 can be between the first holding groove 1122 and an end 31 the rotating shaft 3 be arranged.

[0044] The other end32 the rotating shaft 3 can through the storage hole 1131 the second partition wall 113 with the compression mechanism 4 be connected.

[0045] If the other end 32 the rotating shaft 3 from a first section 321 , which passes through the second partition wall 113 stored, and a second section (eccentric bushing) 322 , which is connected to the compression mechanism 4 is connected, exists, the first section can 321 through a second warehouse 72 , which is in the storage hole 1131 the second partition wall 113 is provided, be rotatably mounted, and the second section (eccentric bushing) 322 can be achieved through a third storage area 73 , which is in the compression mechanism 4 It is provided and must be rotatably mounted.

[0046] The storage hole 1131 the second partition wall 113can be used with a second retaining groove 1132 be formed into which the second camp 72 and the first section 321 the other end 32 the rotating shaft 3 are inserted, and the second camp 72 can be used between the second holding groove 1132 and the first section 321 at the other end 32 the rotating shaft 3 be inserted.

[0047] The compression mechanism 4 can a circumferential spiral 42 include, which will be described later, and a head start 423 exhibit, into which the third camp 73 and the second section (eccentric bushing) 322 at the other end 32 the rotating shaft 3 are inserted, and the third camp 73 can be between the lead 423 and the second section (eccentric bushing) 322 the other end 32 the rotating shaft 3 be inserted.

[0048] The fixed spiral 41 , which are in the compression mechanism 4 It is included, can be firmly attached to the second partition wall 113 on the opposite side of the engine 2 be connected, and the circumferential spiral 42 , which are in the compression mechanism 4 Included is, can be used between the second partition wall 113 and the fixed spiral 41 in interaction with the fixed spiral 41 to define two pairs of compression chambers, and to define the rotating shaft 3 to go around.

[0049] The fixed spiral 41 can a fixed end plate 411 include a plate-shaped component and a fixed band. 421 , which is formed by a compressed surface of the fixed end plate 411 protrudes, in order to be surrounded by a band 422 , which will be described later, the circumferential spiral 42to intervene.

[0050] The fixed end plate 411 can an outlet opening 413 exhibiting a space formed in the middle of it, so that the refrigerant being compressed in the compression chamber is released from the outlet opening. 413 through the fixed end plate 411 is released. The outlet opening 413 can communicate with an outlet space located between the fixed spiral 41 and the third case 13 is defined.

[0051] The circumferential spiral 42 can a circumferential end plate 421 include a plate-shaped design and a surrounding band 422 , which is formed by a compacted surface of the surrounding end plate 421 protrudes in order to be connected to the fixed band 412 to intervene and define the compression chamber.

[0052] The surrounding end plate 421 can use the advantage 423be formed, opposite the circulating band 422 for inserting the rotary shaft 3 which stands out.

[0053] If in the scroll compressor according to the present embodiment, which has such a configuration, the motor 2 When electrical energy is supplied, the rotating shaft can 3 a rotational force on the rotating spiral 42 transferred while together with the rotor 22 rotates. The rotating spiral 42 surrounds the second section (eccentric bushing) 322 the rotating shaft 3 This allows the volume of the compression chambers to decrease while the unit continues to move towards its center. In this case, a refrigerant can enter through a refrigerant inlet (not shown) located in the annular wall. 11a of the first case 11The refrigerant is formed and introduced into the engine compartment. The refrigerant in the engine compartment can be accessed through a refrigerant inlet (not shown) located in the second bulkhead. 113 of the first case 11 The refrigerant is drawn into the compression chambers. As it flows into the compression chambers along the flow paths towards the center of the chambers, it is compressed and can then exit through the outlet opening. 413 The refrigerant introduced into the outlet chamber can be discharged through a refrigerant outlet located in the third housing. 13 The data is formed, from which the scroll compressor is omitted. This series of processes is repeated.

[0054] In these processes, the rotating shaft can 3 from the first, second, and third camp 71 , 72 and 73be rotatably mounted. Since the second bearing 72 The applied load is significantly greater than the load on the first and third bearings. 71 and 73 applied load, the second bearing 72 simply be damaged.

[0055] To mitigate the damage to the second warehouse 72 To avoid this, the second warehouse can be used. 72 as a bearing with a higher load-bearing capacity than the first and third bearings 71 and 73 be configured, but this will affect the cost, size, and weight of the second bearing. 72 increase. Ultimately, the overall cost, size, and weight of the scroll compactor may increase.

[0056] In light of this point, the second camp 72 be formed at a predetermined position to prevent damage to the second bearing 72 to avoid this by reducing the load applied in the present embodiment.

[0057] In detail, the information on the second camp 72 applied load a load that passes through the rotating shaft 3 to the second camp 72 is applied, and closely associated with a torque applied to the rotating shaft 3 is applied, a reaction force that is attached to the rotating shaft 3 in the compression process of a refrigerant by a compression mechanism 4 , and a positional relationship between a point of application of the rotational force, a point of application of the rotational force, and a support point of the rotating shaft 3 is connected.

[0058] To reach the second camp 72 To reduce the applied load, it is therefore necessary to reduce the rotational force and the reaction force, or the positional relationship between the application point of the rotational force, the application point of the reaction force and the bearing point of the rotating shaft. 3 to adapt.

[0059] However, reducing the rotational force and reaction force is not preferable because it impairs the compaction performance. Given this point, it is possible to consider the second bearing. 72 to reduce the applied load by changing the positional relationship between the application point of the rotational force, the application point of the reaction force, and the bearing point of the rotating shaft. 3 is adapted in the present version.

[0060] Assuming that the center of the first camp 71 The first bearing center CB1 is the center of the second bearing. 72 a second storage center CB2 is the middle of the third camp 73 a third camp center CB3 is and the center of the rotor 22 of the engine 2 a motor center CM in the extension direction of the rotating shaft 3 (in the horizontal direction of Fig. 1) In detail, the motor center CM can be an application point of the torque, the third bearing center CB3 can be one application point of the reaction force and the first bearing center CB1 and the second camp center CB2 Can bearing points of the rotating shaft 3 be.

[0061] The first bearing center CB1 and the third bearing center CB3 can be formed such that the distance between the first bearing center CB1 and the third bearing center CB3 (hereinafter referred to as "first distance") D1 a predetermined distance, so that the length of the scroll compressor (the horizontal length of Fig. 1) is not greater than a predetermined value. Here, the distance is a distance in the extension direction of the rotating shaft. 3 (in the horizontal direction of Fig. 1) Measured distance.

[0062] The motor center CM can be formed such that the distance between the motor center CM and the third bearing center CB3 (hereinafter referred to as "distance") 1 - 2 ) D12 is longer than the distance between the engine center CM and the first bearing center CB1 (hereinafter referred to as "distance 1-1") D11 , to achieve the maximum engine performance 2 in the engine compartment where the engine 2 is limited in its ability to be obtained. That is to say, the engine 2 must be formed in such a way as not to form the first and second partition walls 112 and 113 to disturb, and the engine center CM is preferably in the middle between the first partition wall 112 and the second partition 113 positioned to achieve the maximum power (size) of the motor 2 to obtain while this restriction is met, in which case the distance 1 - 2 D12 longer than the distance1 - 1 D11 may be.

[0063] The motor center CM is an application point of the torque and the force acting on the first and third bearings. 71 and 73 The applied loads are changed depending on where the motor center CM is located in the extension direction of the rotating shaft. 3 is positioned. According to the result of an experiment, the motor center CM can preferably be formed such that the distance 1 - 2 D12 1.9 times greater than the distance 1 - 1 D11 , to sum the amount allocated to the first and third camps 71 , 73 applied loads L1 + L3, as in Fig. 2 represents, to maximize.

[0064] The second camp center CB2 can be formed so that the distance between the second bearing center CB2 and the engine center (hereinafter referred to as "distance 1-2-1") D121longer than the distance between the second bearing center CB2 and the third camp center CB3 (hereinafter referred to as "distance 1-2-2") D122 is to reduce the load on the second bearing 72 is applied in the state in which the third bearing 73 and reduce the engine center CM as described above.

[0065] That is, the second camp center CB2 is a section to which a load for the rotational force (hereinafter referred to as the "first load") and a load for the reaction force (hereinafter referred to as the "second load") are applied simultaneously. The first load can be proportional to the magnitude of the rotational force, and the distance 1 - 2 - 1 D121 and the second load can be proportional to the strength of the reaction force and the distance 1 - 2 - 2 D122 be. Since the second bearing center is thus CB2 closer to the first camp 71 moving the distance 1 - 2 - 1 D121 to be reduced in order to reduce the initial load, while the distance 1 - 2 - 2 D122 It can be increased to increase the second load. Since, on the other hand, the second bearing center CB2 closer to the third camp 73 moving the distance 1 - 2 - 2 D122 to be reduced in order to reduce the second load, while the distance 1 - 2 - 1 D121 It can be increased to increase the first load. However, the load on the second bearing is 72 applied total load significantly different from the distance 1 - 2 - 2 D122 affected as by the distance 1 - 2 - 1 D121 , because the reaction force is greater than the rotational force. Therefore, if the distance 1 -2 - 1 D121 longer than the distance 1 - 2 - 2 D122 Is it possible to reduce the total load on the second bearing? 72 is applied.

[0066] However, it can be seen that if the ratio of the distance 1 - 2 - 1 D121 at that distance 1 - 2 - 1 D12 is outside a predetermined area (if the distance 1 - 2 - 1 D121 excessively longer than the distance 1 - 2 - 2 D122 is), which is on the second camp 72 The total applied load is rather increased. That is, according to the result of an experiment, it can be seen that in the second bearing 72 total applied load L2 the ratio of the distance 1 - 2 - 1 D121 at that distance 1 -2 D12 gradually reduced to 0.62 (=1.17 / 1.9) or less, reduced to more than 0.62 and 0.64 in a stepped form, and gradually increased again to more than 0.64, as in Fig. 3 represents. Thus, it may be preferable that the second bearing center CB2 is formed, such that the ratio of the distance 1 - 2 - 1 at that distance 1 - 2 D12 in the range of 0.62 to 0.64, to the second bearing 72 Total applied load L2 to noticeably reduce, and so that the ratio of the distance 1 - 2 - 1 D121 in the 1-2 distance 0.64 is to the second bearing 72 Total applied load L2 to minimize. That is, it may be preferable for the second bearing center to be CB2, so that the distance 1 - 2 - 1 D1211.17 to 1.22 times larger than the distance 1 - 1 D11 is, and so that the distance 1 - 2 - 1 D121 1.22 times greater than the distance 1 - 1 D11 is.

[0067] If the scroll compressor is configured according to the embodiment of the present disclosure, such that the first spacing D1 a predetermined distance, the distance 1 - 2 D12 longer than the distance 1 - 1 is and the distance 1 - 2 - 1 D121 longer than the distance 1 - 2 - 2 D122 Is it possible to achieve the maximum power output of the motor? 2 to obtain those who are on the first and third camps 71 and 73 to minimize the applied loads, and those on the second bearing 72 to reduce the applied load in order to minimize damage to the second bearing72 to avoid within the predetermined total length of the scroll compressor.

[0068] In the case where the second camp 72 Since it is used as a bearing that has the same conventional load-bearing capacity, it is therefore possible to improve the reliability of the second bearing. 72 and to improve the scroll compressor in general.

[0069] Meanwhile, the second camp 72 be replaced with a bearing that has a lower load-bearing capacity compared to the state of the art. That is to say, the second bearing 72 can be used as a bearing with the same load-bearing capacity as at least one of the first or third bearings 71 and 73 be formed. Consequently, it is possible to suppress an increase in cost, size, and weight due to the bearing. However, in terms of safety, it may be preferable for the second bearing to be 72a greater load-bearing capacity than the first and third bearings 71 and 73 exhibits, although its load-bearing capacity is smaller compared to the state of the art.

[0070] The distance 1 - 2 - 1 D121 is longer than the distance 1 - 2 - 2 D122 , provided that the first distance D1 the predetermined distance is and the distance 1 - 2 D12 longer than the distance 1 - 1 D11 in the above embodiment, but the present embodiment is not limited to it.

[0071] For example, it is possible to place the items on the second storage area. 72 to reduce the applied load, as long as the distance 1 - 2 - 2 D122 shorter than the sum of the distances 1 - 1 D11 and the distance 1 - 2 -1 D121 is. To the second camp 72 To further reduce the applied load, it may be preferable in this case that the sum of the distance 1 - 1 D11 and the distance 1 - 2 - 1 D121 in a range from 2.97 (=(1 + 1.17) / (1.9 - 1.17)) to 3.27 times (= (1 + 1.22) / (1.9 - 1.22)) is greater than the distance 1 - 2 -2 D122.

[0072] Alternatively, it is possible to place them on the second storage area. 72 to reduce the applied load, as long as the distance 1 - 2 - 2 D122 shorter than the distance 1 - 2 - 1 D121 However, in this case it may be preferable that the distance 1 - 2 - 1 D121 in a range from 1.60 to (= 1.17 / (1.9 - 1.17)) to 1.8 times (= 1.22 / (1.9 - 1.22)) is greater than the distance 1 - 2 -2 D122 .

[0073] Alternatively, it is possible to place them on the second storage area. 72 to reduce the applied load, as long as the second bearing 72 adjacent to the compression chambers, without the distance relationship between the second bearing 72 and the third camp 73 to be taken into account. However, in this case, the second section (eccentric bushing) 322 , the one at the second camp 72 overlapping position rotates, the second bearing 72 in the axial direction of the rotating shaft 3 disrupt. To avoid this point, the second bearing must 72 therefore, as close as possible to the compression chambers within an area where the second section (eccentric bushing) is not located. 322 disrupts. For this purpose, the second retaining groove can be used. 1132 from the surface of the second partition 113be set back facing the compression chambers, and the second bearing 72 can be formed as low as possible within an area where it does not lead to the second section (eccentric bushing) 322 (in the axial direction) from the second retaining groove 1132 stands out. INDUSTRIAL APPLICABILITY

[0074] The present disclosure provides a scroll compressor capable of preventing damage to a bearing that supports a rotating shaft between a motor and a rotating spiral.

[0075] Additionally, another objective of the present disclosure is to provide a scroll compactor that is able to avoid an increase in cost, size and weight due to a bearing. QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] KR 1020160081675 [0006, 0007]

Claims

[1] Scroll compressors, including: a shell (1); a motor (2) to generate a driving force in the shell (1); a rotating shaft (3) which is rotated by the motor (2); a rotating spiral (42) that rotates around the rotating shaft (3); a fixed spiral (41) which together with the rotating spiral (42) forms a compression chamber; a first bearing (71) which rotatably supports the rotating shaft (3) relative to the casing (1) on one side of the rotating shaft (3) in relation to the motor (2); a second bearing (72) which rotatably supports the rotating shaft (3) relative to the casing (1) on the other side of the rotating shaft (3) in relation to the motor (2); a third bearing (73) which rotatably supports the rotating shaft (3) relative to the circumferential spiral (42) on the opposite side of the first bearing (71) in relation to the second bearing (71), wherein: assuming that the center of the first bearing (71) is a first bearing center (CB1), the center of the second bearing (72) is a second bearing center (CB2), the center of the third bearing (73) is a third bearing center (CB3), and the center of a rotor (22) of the motor (2) is a motor center (CM) in an extension direction of the rotating shaft (3), a distance between the first bearing center (CB1) and the third bearing center (CB3) (D1) is a predetermined distance; a distance between the motor center (CM) and the third bearing center (CB3) (D12) is longer than a distance between the motor center (CM) and the first bearing center (CB1) (D11); and a distance between the second bearing center (CB2) and the motor center (CM) (D121) is longer than the distance between the second bearing center (CB2) and the third bearing center (CB3) (D122). [2] Scroll compressor according to claim 1, wherein the distance between the motor center (CM) and the third bearing center (CB3) (D12) is 1.9 times greater than the distance between the motor center (CM) and the first bearing center (CB1) (D11). [3] Scroll compressor according to claim 2, wherein the distance between the second bearing center (CB2) and the motor center (CM) (D121) is in a range of 1.17 to 1.22 times greater than the distance between the motor center (CM) and the first bearing center (CB1) (D11). [4] Scroll compressor according to claim 3, wherein the distance between the second bearing center (CB2) and the motor center (CM) (D121) is 1.22 times greater than the distance between the motor center (CM) and the first bearing center (CB1) (D11). [5] Scroll compressor according to any one of claims 1 to 4, wherein the second bearing (72) has the same load-bearing capacity as at least one of the first and third bearings (71 and 73). [6] Scroll compactors, comprehensive: a shell (1); a motor (2) to generate a driving force in the shell (1); a rotating shaft (3) which is rotated by the motor (2); a rotating spiral (42) that rotates around the rotating shaft (3); a fixed spiral (41) which together with the rotating spiral (42) forms a compression chamber; a first bearing (71) which rotatably supports the rotating shaft (3) relative to the casing (1) on one side of the rotating shaft (3) in relation to the motor (2); a second bearing (72) which rotatably supports the rotating shaft (3) relative to the casing (1) on the other side of the rotating shaft (3) in relation to the motor (2); a third bearing (73) which rotatably supports the rotating shaft (3) relative to the rotating spiral (42) on the opposite side of the first bearing (71) in relation to the second bearing (71), assuming that the center of the first bearing (71) is a first bearing center (CB1), the center of the second bearing (72) is a second bearing center (CB2), and the center of the third bearing (73) is a third bearing center (CB3) in an extension direction of the rotating shaft (3), wherein a distance between the second bearing center (CB2) and the third bearing center (CB3) (D122) is shorter than the distance between the second bearing center (CB2) and the first bearing center (CB1) (a sum of D11 and D121). [7] Scroll compressor according to claim 6, wherein the distance between the second bearing center (CB2) and the first bearing center (CB1) (a sum of D11 and D121) is in a range of 2.97 to 3.27 times greater than the distance between the second bearing center (CB2) and the third bearing center (CB3) (D122). [8] Scroll compressor according to claim 6, wherein assuming that the center of a rotor (22) of the motor (2) is a motor center (CM), the distance between the second bearing center (CB2) and the third bearing center (CB3) (D122) is shorter than a distance between the second bearing center (CB2) and the motor center (CM) (D121). [9] Scroll compressor according to claim 8, wherein the distance between the second bearing center (CB2) and the motor center (CM) (D121) is in a range of 1.60 to 1.80 times greater than the distance between the second bearing center (CB2) and the third bearing center (CB3) (D122). [10] Scroll compressor according to claim 8, wherein the distance between the motor center (CM) and the third bearing center (CB3) (D12) is longer than the distance between the motor center (CM) and the first bearing center (CB1) (D11). [11] Scroll compressor according to claim 10, wherein the distance between the motor center (CM) and the third bearing center (CB3) (D12) is 1.9 times greater than the distance between the motor center (CM) and the first bearing center (CB1) (D11). [12] Scroll compressor according to claim 8, wherein the distance between the first bearing center (CB1) and the third bearing center (CB3) (D1) is a predetermined distance. [13] Scroll compactors, including: a shell (1); a motor (2) to generate a driving force in the shell (1); a rotating shaft (3) which is rotated by the motor (2); a rotating spiral (42) that rotates around the rotating shaft (3); a fixed spiral (41) which together with the rotating spiral (42) forms a compression chamber; a second bearing (72) which rotatably supports the rotating shaft (3) between the motor (2) and the compression chamber, wherein: the rotating shaft (3) comprises an eccentric bushing (322) which rotates in an axial direction of the rotating shaft (3) at a position overlapping with the second bearing (72); and the second bearing (72) is located as close as possible to the compression chamber within an area where it does not obstruct the eccentric bushing (322). [14] Scroll compactors, including: a shell (1); a motor (2) to generate a driving force in the shell (1); a rotating shaft (3) which is rotated by the motor (2); a rotating spiral (42) which rotates around the rotating shaft (3); a fixed spiral (41) which together with the circumferential spiral (42) defines a compression chamber, wherein the shell (1) comprises the following: a first partition (112) to separate a space for housing the motor (2) from a space for housing an inverter (5) for controlling the motor (2); and a second partition (113) to separate the space for accommodating the engine (2) from a space for providing the compression chamber, and wherein: the first partition wall (112) is formed with a first retaining groove (1122) into which a first bearing (71) for supporting one end of the rotating shaft (3) is inserted; the second partition (113) is formed with a second retaining groove (1132) into which a second bearing (72) is inserted for supporting the other end of the rotating shaft (3); and the second retaining groove (1132) is recessed from a surface of the second partition wall 113, which faces the compression chamber. [15] Scroll compressor according to claim 14, wherein the second bearing (72) is formed as low as possible within a region in which it does not protrude in an axial direction from the second retaining groove (1132).