Scroll compressor and air conditioner

Abstract

The invention provides a scroll compressor and an air conditioner, the scroll compressor comprises a driving shaft, an eccentric crank pin and a bushing, the eccentric crank pin is arranged at the end part of the driving shaft, and a first driving surface is arranged on the eccentric crank pin. The bushing is provided with a mounting hole, the eccentric crank pin is inserted into the mounting hole, a first driven surface is arranged in the mounting hole, and the first driving surface is used for pushing the first driven surface under the condition that the driving shaft rotates reversely. In the radial direction of the driving shaft, the distance between the axis of the driving shaft and the first driving face is L1, the distance between the axis of the lining and the first driven face is H1, and L1 and H1 meet the condition that L1 is larger than H1. The distance between the axis of the driving shaft and the first driving surface is larger than the distance between the axis of the bushing and the first driven surface, and the component force of the force applied to the orbiting scroll in the radial direction is larger, so that the contact force between the orbiting scroll and the static scroll can be improved, the time required by the compressor from reverse rotation to shutdown to restart is shorter, the abrasion problem of parts is reduced, and the service life of the compressor is prolonged. The reliability of the compressor is improved.

Description

Technical Field

[0001] This invention belongs to the field of compressor technology, specifically, it relates to a scroll compressor and an air conditioner. Background Technology

[0002] If a single-phase scroll compressor is powered back to operation within a very short time after a power outage, the compressor will reverse. During this reversal, the compressor will not circulate refrigerant, causing the air conditioner to stop cooling. Furthermore, prolonged reversal can affect the reliability of the compressor. Summary of the Invention

[0003] The present invention aims to solve one of the technical problems existing in the prior art or related technologies.

[0004] In view of this, in a first aspect, the present invention proposes a scroll compressor, comprising: a drive shaft; an eccentric crank pin disposed at the end of the drive shaft, the eccentric crank pin being eccentrically disposed relative to the drive shaft, the eccentric crank pin having a first driving surface; a bushing having a mounting hole, the eccentric crank pin being inserted into the mounting hole, the mounting hole having a first driven surface, the first driving surface being used to push the first driven surface when the drive shaft reverses; wherein, along the radial direction of the drive shaft, the distance between the axis of the drive shaft and the first driving surface is L1, the distance between the axis of the bushing and the first driven surface is H1, and L1 and H1 satisfy L1 > H1.

[0005] The scroll compressor provided by this invention has an eccentric crank pin mounted on a drive shaft. The drive shaft can drive the eccentric crank pin to rotate. The eccentric crank pin is inserted into the mounting hole of the bushing, so that the eccentric crank pin can drive the bushing to rotate. The bushing is used to assemble with the moving scroll in the scroll compressor, so that the bushing can drive the moving scroll to move. The moving scroll and the fixed scroll in the scroll compressor are used to compress the refrigerant.

[0006] In certain abnormal situations, such as a sudden power outage followed by a very short period of power restoration, the compressor motor may reverse. In this case, the motor drives the drive shaft and eccentric crank pin to rotate in the opposite direction. The first driving surface of the eccentric crank pin engages with the first driven surface of the unloading bushing. Through this structure, the eccentric crank pin can drive the unloading bushing to rotate in the opposite direction.

[0007] In the above scenario, the motor driving the compressor to rotate in reverse is an abnormal condition. In this case, the compressor does not compress the refrigerant, causing the air conditioning system to fail to cool. When this happens, very little refrigerant circulates inside the compressor, resulting in insufficient refrigerant to cool the motor. Typically, the motor needs to heat up to the temperature at which the protector opens, triggering the protector and stopping the motor from reversing. Subsequently, the motor cools down naturally until its temperature drops to the protector's closing temperature, at which point the compressor can restart normally.

[0008] When the compressor rotates in reverse, the moving and fixed scrolls change from compressing gas to expanding gas, which is equivalent to creating a vacuum inside the scroll. When the compressor experiences this reverse rotation anomaly, it typically takes about an hour from reversal to shutdown and then restart. An air conditioning system failing to cool for an extended period will cause customer complaints. Prolonged compressor reversal may also cause wear and tear on components.

[0009] During the operation of the moving scroll relative to the fixed scroll, the greater the reaction force of the moving scroll, the better the sealing effect between the moving scroll and the fixed scroll.

[0010] Specifically, the greater the radial interaction force between the moving and fixed scroll plates, the better the sealing effect between them. When the distance between the drive shaft axis and the first drive surface is greater than the distance between the bushing axis and the first driven surface, the radial component of the force applied to the moving scroll plate is larger, thereby improving the contact force between the moving and fixed scroll plates. The greater the force exerted by the moving scroll plate on the fixed scroll plate, the greater the work consumed by the moving scroll plate. At this time, the motor current is larger, the motor heat generation is increased, the heating rate is faster, the time for the motor to reach the protector opening temperature is shorter, and the time required for the compressor to go from reverse rotation to shutdown and then to restart is shorter. This avoids the problem of the air conditioning system failing to cool for a long time, reduces the wear of parts, and helps improve the reliability of the compressor.

[0011] In addition, the scroll compressor according to the above-described technical solution provided by the present invention may also have the following additional technical features:

[0012] In some technical solutions, optionally, the eccentric crank pin is also provided with a second driving surface, and the mounting hole is also provided with a second driven surface. When the drive shaft rotates forward, the second driving surface is used to push the second driven surface. The distance between the axis of the drive shaft and the second driving surface along the radial direction of the drive shaft is L2, and the distance between the axis of the bushing and the second driven surface is H2. L2 and H2 satisfy L2 > H2.

[0013] When the distance between the drive shaft axis and the second drive surface is greater than the distance between the bushing axis and the second driven surface, the radial component of the moving scroll is larger during the forward rotation of the motor, thereby increasing the contact force between the moving scroll and the fixed scroll. The greater the force exerted by the moving scroll on the fixed scroll, the better the sealing performance between the moving scroll and the fixed scroll, avoiding refrigerant leakage and improving the performance of the scroll compressor.

[0014] In some technical solutions, optionally, there is an included angle between the first driving surface and the second driving surface.

[0015] The eccentric crank pin has an included angle between its first and second driving surfaces, meaning it has non-parallel first and second driving surfaces. This allows the compressor to maintain a suitable radial sealing force while also possessing a large radial sealing force during reverse rotation. This enables the compressor to generate a larger operating current during reverse rotation under certain abnormal conditions, allowing the compressor protector to activate more quickly and improving compressor reliability.

[0016] In some technical solutions, optionally, when the drive shaft rotates forward, the second driving surface and the second driven surface are in contact; when the drive shaft rotates in reverse, the first driving surface and the first driven surface are in contact.

[0017] When the compressor is rotating forward, the drive shaft also rotates forward. During this process, the second drive surface pushes the second driven surface. In this design, the second drive surface and the second driven surface are in contact with each other, that is, the second drive surface and the second driven surface are parallel to each other, so that the second drive surface and the second driven surface can be in close contact. They have a large contact area, which is beneficial to improving the driving stability of the eccentric crank pin on the bushing.

[0018] Similarly, when the compressor reverses, the drive shaft reverses. During this process, the first drive surface pushes the first driven surface. In this solution, the first drive surface and the first driven surface are in contact with each other, that is, the first drive surface and the first driven surface are parallel to each other, so that the first drive surface and the first driven surface can be in close contact. The two have a large contact area, which is beneficial to improving the driving stability of the eccentric crank pin to the bushing.

[0019] It should be noted that the first driving surface and the first driven surface are parallel to each other, and the second driving surface and the second driven surface are parallel to each other. When there is an angle between the first driving surface and the second driving surface, there is also an angle between the first driven surface and the second driven surface.

[0020] In some technical solutions, optionally, when the drive shaft rotates forward, the second driving surface and the second driven surface separate; when the drive shaft rotates in reverse, the first driving surface and the first driven surface separate.

[0021] When the drive shaft reverses, the first driving surface and the first driven surface are in contact, allowing the first driving surface to push the first driven surface. At this time, the second driving surface and the second driven surface separate, avoiding interference between the second driving surface and the second driven surface, which would affect the force applied to the moving scroll when the motor reverses.

[0022] Similarly, when the drive shaft rotates forward, the second driving surface and the second driven surface are in contact, allowing the second driving surface to push the second driven surface. At this time, the first driving surface and the first driven surface separate, avoiding interference between the first driving surface and the first driven surface, which would affect the force applied to the moving scroll when the motor rotates forward.

[0023] In some technical solutions, optionally, a first arc-shaped surface is provided between the first side of the first driving surface and the second driving surface; a second arc-shaped surface is provided between the second side of the first driving surface and the second driving surface, and the first arc-shaped surface and the second arc-shaped surface are concentrically arranged.

[0024] The two sides of the first driving surface are connected to the second driving surface through arc-shaped surfaces. The arc-shaped surfaces on both sides of the first driving surface are concentrically set, that is, the axis of the first arc-shaped surface and the axis of the second arc-shaped surface are collinear, without the need to design the axis of the first arc-shaped surface and the second arc-shaped surface separately, which helps to reduce the machining difficulty of the eccentric crank pin.

[0025] In some technical solutions, optionally, both the first arc-shaped surface and the second arc-shaped surface are spaced apart from the inner wall of the mounting hole.

[0026] Neither the first arc-shaped surface nor the second arc-shaped surface is in contact with the inner wall of the mounting hole. During the forward or reverse rotation of the drive shaft, the first arc-shaped surface and the second arc-shaped surface will not come into contact with the inner wall of the mounting hole, thereby avoiding interference between the first arc-shaped surface and the second arc-shaped surface and the inner wall of the mounting hole, and preventing the force applied to the moving scroll when the motor rotates from being affected.

[0027] In some technical solutions, optionally, the first driving angle is set as α1, and the eccentricity of the scroll compressor is D, where α1 = arcsin[(L1-H1) / D].

[0028] The eccentricity of the scroll compressor is the distance between the axis of the drive shaft and the axis of the bushing. During the reverse rotation of the motor, there is a contact force between the moving scroll and the fixed scroll. The eccentric crank pin applies a driving force to the bushing. The radial component of the driving force is equal to the driving force × sinα1. The contact force is proportional to the radial component of the driving force. When L1 is greater than H1, α1 > 0, and the radial component of the driving force is positive. Therefore, the moving scroll will apply a larger contact force to the fixed scroll, thereby increasing the power consumed by the moving scroll and facilitating the rapid shutdown of the motor.

[0029] In some technical solutions, the second driving angle can be optionally set as α2, and the eccentricity of the scroll compressor can be set as D, where α2 = arcsin[(L2-H2) / D].

[0030] The eccentricity of the scroll compressor is the distance between the axis of the drive shaft and the axis of the bushing. During the forward rotation of the motor, there is a contact force between the moving scroll and the fixed scroll. The eccentric crank pin applies a driving force to the bushing. The radial component of the driving force is equal to the driving force × sinα2. The contact force is proportional to the radial component of the driving force. When L2 is greater than H2, α2 > 0, and the radial component of the driving force is positive. Therefore, the moving scroll will apply a larger contact force to the fixed scroll, improving the fit between the moving scroll and the fixed scroll.

[0031] Secondly, the present invention provides an air conditioner comprising a scroll compressor as described in the above technical solution. Therefore, the air conditioner provided by the present invention has all the beneficial effects of the scroll compressor provided in the above technical solution.

[0032] Additional aspects and advantages of the invention will become apparent in the following description or may be learned by practice of the invention. Attached Figure Description

[0033] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0034] Figure 1 A schematic diagram of the drive shaft, eccentric crank pin, and bushing in an embodiment of the present invention is shown;

[0035] Figure 2 A schematic diagram of the eccentric crank pin and bushing in an embodiment of the present invention is shown;

[0036] Figure 3 A schematic diagram of the eccentric crank pin in an embodiment of the present invention is shown;

[0037] Figure 4 A schematic diagram of the bushing structure in an embodiment of the present invention is shown;

[0038] Figure 5 A schematic diagram showing the engagement of the eccentric crank pin and bushing when the motor reverses in an embodiment of the present invention is shown;

[0039] Figure 6 A schematic diagram showing the engagement of the eccentric crank pin and bushing when the motor rotates forward is shown in an embodiment of the present invention;

[0040] Figure 7 A schematic diagram of the scroll compressor in an embodiment of the present invention is shown.

[0041] Figure label:

[0042] 100 Scroll compressor, 110 drive shaft, 120 eccentric crank pin, 121 first drive surface, 122 second drive surface, 123 first arc-shaped surface, 124 second arc-shaped surface, 130 bushing, 131 mounting hole, 132 first driven surface, 133 second driven surface, 140 fixed scroll, 150 moving scroll, 160 bearing housing, 170 motor, 180 frame. Detailed Implementation

[0043] To better understand the above-mentioned objectives, features, and advantages of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0044] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and therefore the scope of protection of the invention is not limited to the specific embodiments disclosed below.

[0045] The following reference Figures 1 to 7 A scroll compressor and an air conditioner are described according to some embodiments of the present invention.

[0046] Combination Figure 1 , Figure 2 , Figure 3 , Figure 4 and Figure 7 As shown, in an embodiment of the present invention, a scroll compressor 100 is provided, comprising: a drive shaft 110, an eccentric crank pin 120, and a bushing 130. The eccentric crank pin 120 is disposed at the end of the drive shaft 110, and is eccentrically disposed relative to the drive shaft 110. A first driving surface 121 is provided on the eccentric crank pin 120. The bushing 130 is provided with a mounting hole 131, and the eccentric crank pin 120 is inserted into the mounting hole 131. A first driven surface 132 is provided in the mounting hole 131. When the drive shaft 110 reverses direction, the first driving surface 121 is used to push the first driven surface 132. Along the radial direction of the drive shaft 110 ( Figure 1 The arrow at point R points to the axis of drive shaft 110. Figure 2 The arrow at reference numeral O1 points to the axis of drive shaft 110, and the distance between it and the first drive surface 121 is L1. The axis of bushing 130 ( Figure 2 The arrow at point O2 points to the axis of bushing 130. The distance between the arrow and the first driven surface 132 is H1. L1 and H1 satisfy L1 > H1.

[0047] The scroll compressor 100 provided by the present invention has an eccentric crank pin 120 disposed on a drive shaft 110. The drive shaft 110 can drive the eccentric crank pin 120 to rotate. The eccentric crank pin 120 is inserted into the mounting hole 131 of the bushing 130, so that the eccentric crank pin 120 can drive the bushing 130 to rotate. The bushing 130 is used to assemble with the moving scroll 150 in the scroll compressor 100, so that the bushing 130 can drive the moving scroll 150 to move. The moving scroll 150 and the fixed scroll 140 in the scroll compressor 100 are used to compress refrigerant.

[0048] In certain abnormal situations, such as a sudden power outage followed by a very short time of power restoration, the compressor motor 170 will reverse. At this time, the motor 170 drives the drive shaft 110 and the eccentric crank pin 120 to rotate in the opposite direction. The first driving surface 121 of the eccentric crank pin 120 engages with the first driven surface 132 of the unloading bushing 130. Through this structure, the eccentric crank pin 120 can drive the unloading bushing 130 to rotate in the opposite direction.

[0049] In the above situation, the motor 170 driving the compressor to rotate in reverse is an abnormal condition. In this case, the compressor does not compress the refrigerant, causing the air conditioning system to fail to cool. When this happens, very little refrigerant circulates inside the compressor, and there is insufficient refrigerant to cool the motor 170. Typically, the motor 170 needs to heat up to the protector's activation temperature to trigger the protector and stop the motor 170 from reversing. Subsequently, the motor 170 cools down naturally until its temperature drops to the protector's shutdown temperature, at which point the compressor can restart normally.

[0050] When the compressor rotates in reverse, the moving scroll 150 and the fixed scroll 140 change from compressing gas to expanding gas, which is equivalent to evacuating the inside of the scroll. When the compressor experiences an abnormal reverse rotation, it usually takes about one hour from reversal to shutdown and then restart. An air conditioning system failing to cool for an extended period will cause customer complaints. Prolonged compressor reversal may also cause wear and tear on components.

[0051] During the operation of the moving scroll 150 relative to the fixed scroll 140, the greater the reaction force of the moving scroll 150, the better the sealing effect between the moving scroll 150 and the fixed scroll 140.

[0052] Specifically, the greater the radial interaction force between the moving scroll 150 and the fixed scroll 140, the better the sealing effect between them. When the distance between the axis of the drive shaft 110 and the first drive surface 121 is greater than the distance between the axis of the bushing 130 and the first driven surface 132, the radial component of the force applied to the moving scroll 150 is larger, thereby improving the contact force between the moving scroll 150 and the fixed scroll 140. The greater the force exerted by the moving scroll 150 on the fixed scroll 140, the greater the work consumed by the moving scroll 150. At this time, the current of the motor 170 is larger, the heat generated by the motor 170 increases, the heating rate is faster, and the time it takes for the motor 170 to heat up to the protector opening temperature is shorter. The time required for the compressor to go from reversing to stopping and then restarting is shorter, avoiding the problem of the air conditioning system failing to cool for a long time, reducing the wear of parts, and improving the reliability of the compressor.

[0053] It should be noted that when the drive shaft 110 rotates in the reverse direction, the direction of the reverse driving force is opposite to the rotation direction of the moving scroll 150, causing the sidewall of the moving scroll 150 to not fit well with the sidewall of the fixed scroll 140, resulting in significant radial leakage. Therefore, the compressor current is usually lower when it reverses, the motor 170 generates less heat and heats up more slowly, and the time it takes for the motor 170 to reach the temperature required for the protector to open is longer. This embodiment solves the above problems by setting the relationship between L1 and H1.

[0054] like Figure 7 As shown, the drive shaft 110 is connected to the motor 170, which is used to drive the drive shaft 110 to rotate forward or in reverse. The scroll compressor 100 also includes a bearing housing 160 and a frame 180. The bushing 130 is mounted on the bearing housing 160, and the frame 180 is used to support the drive shaft 110.

[0055] In some embodiments, optionally, the eccentric crank pin 120 is further provided with a second driving surface 122, and the mounting hole 131 is further provided with a second driven surface 133. When the drive shaft 110 rotates forward, the second driving surface 122 is used to push the second driven surface 133. Along the radial direction of the drive shaft 110, the distance between the axis of the drive shaft 110 and the second driving surface 122 is L2, and the distance between the axis of the bushing 130 and the second driven surface 133 is H2. L2 and H2 satisfy the condition that L2 > H2.

[0056] When the distance between the axis of the drive shaft 110 and the second drive surface 122 is greater than the distance between the axis of the bushing 130 and the second driven surface 133, the radial component of the force on the moving scroll 150 is larger during the forward rotation of the motor 170, thereby improving the contact force between the moving scroll 150 and the fixed scroll 140. The greater the force exerted by the moving scroll 150 on the fixed scroll 140, the better the sealing performance between the moving scroll 150 and the fixed scroll 140, avoiding refrigerant leakage and improving the performance of the scroll compressor 100.

[0057] like Figure 3 As shown, in some embodiments, optionally, there is an included angle β between the first driving surface 121 and the second driving surface 122.

[0058] The first driving surface 121 and the second driving surface 122 of the eccentric crank pin 120 have an included angle β, that is, the eccentric crank pin 120 has a first driving surface 121 and a second driving surface 122 that are not parallel to each other. This allows the compressor to have a suitable radial sealing force while also having a large radial sealing force when reversing. This enables the compressor to have a large operating current when reversing under certain abnormal conditions, allowing the compressor protector to protect itself as quickly as possible and improving the reliability of the compressor.

[0059] Combination Figure 3 , Figure 4 , Figure 5 and Figure 6 As shown, in some embodiments, optionally, when the drive shaft 110 rotates forward, the second drive surface 122 and the second driven surface 133 are in contact, and when the drive shaft 110 rotates in reverse, the first drive surface 121 and the first driven surface 132 are in contact.

[0060] When the compressor is rotating forward, the drive shaft 110 rotates forward. During this process, the second drive surface 122 pushes the second driven surface 133. In this design, the second drive surface 122 and the second driven surface 133 are in close contact with each other, that is, the second drive surface 122 and the second driven surface 133 are parallel to each other, so that the second drive surface 122 and the second driven surface 133 can be in close contact. They have a large contact area, which is beneficial to improving the driving stability of the eccentric crank pin 120 on the bushing 130.

[0061] Similarly, when the compressor reverses, the drive shaft 110 reverses. During this process, the first drive surface 121 pushes the first driven surface 132. In this solution, the first drive surface 121 and the first driven surface 132 are in close contact with each other, that is, the first drive surface 121 and the first driven surface 132 are parallel to each other, so that the first drive surface 121 and the first driven surface 132 can be in close contact. The two have a large contact area, which is beneficial to improving the driving stability of the eccentric crank pin 120 on the bushing 130.

[0062] It should be noted that the first driving surface 121 and the first driven surface 132 are parallel to each other, and the second driving surface 122 and the second driven surface 133 are parallel to each other. When there is an angle between the first driving surface 121 and the second driving surface 122, there is also an angle between the first driven surface 132 and the second driven surface 133.

[0063] Combination Figure 5 and Figure 6 As shown, in some embodiments, optionally, when the drive shaft 110 rotates forward, the second drive surface 122 and the second driven surface 133 separate. When the drive shaft 110 rotates in reverse, the first drive surface 121 and the first driven surface 132 separate.

[0064] When the drive shaft 110 reverses, the first drive surface 121 and the first driven surface 132 come into contact, so that the first drive surface 121 can push the first driven surface 132. At this time, the second drive surface 122 and the second driven surface 133 separate, so as to avoid the second drive surface 122 and the second driven surface 133 interfering with each other and affecting the force applied to the moving scroll 150 when the motor 170 reverses.

[0065] Similarly, when the drive shaft 110 rotates forward, the second drive surface 122 and the second driven surface 133 are in contact, so that the second drive surface 122 can push the second driven surface 133. At this time, the first drive surface 121 and the first driven surface 132 are separated, so as to avoid the first drive surface 121 and the first driven surface 132 interfering with each other and affecting the force applied to the moving scroll 150 when the motor 170 rotates forward.

[0066] like Figure 3 As shown, in some embodiments, optionally, a first arcuate surface 123 is provided between the first side of the first driving surface 121 and the second driving surface 122, and a second arcuate surface 124 is provided between the second side of the first driving surface 121 and the second driving surface 122, and the first arcuate surface 123 and the second arcuate surface 124 are concentrically arranged.

[0067] The two sides of the first driving surface 121 are connected to the second driving surface 122 through arc-shaped surfaces. The arc-shaped surfaces on both sides of the first driving surface 121 are concentrically arranged, that is, the axis of the first arc-shaped surface 123 and the axis of the second arc-shaped surface 124 are collinear, without the need to design the axis of the first arc-shaped surface 123 and the second arc-shaped surface 124 separately, which helps to reduce the machining difficulty of the eccentric crank pin 120.

[0068] Combination Figure 2 and Figure 3 As shown, in some embodiments, optionally, the first arcuate surface 123 and the second arcuate surface 124 are both spaced apart from the inner wall of the mounting hole 131.

[0069] Neither the first arc-shaped surface 123 nor the second arc-shaped surface 124 is in contact with the inner wall of the mounting hole 131. During the forward or reverse rotation of the drive shaft 110, the first arc-shaped surface 123 and the second arc-shaped surface 124 will not come into contact with the inner wall of the mounting hole 131, thereby avoiding interference between the first arc-shaped surface 123 and the second arc-shaped surface 124 and the inner wall of the mounting hole 131, and preventing the force applied to the moving scroll 150 when the motor 170 rotates.

[0070] Combination Figure 2 and Figure 6 As shown, in some embodiments, optionally, the first drive angle is set to α1, and the eccentricity of the scroll compressor is D, where α1 = arcsin[(L1-H1) / D].

[0071] The eccentricity of the scroll compressor is the distance between the axis of the drive shaft 110 and the axis of the bushing 130. During the reverse rotation of the motor 170, there is a contact force between the moving scroll 150 and the fixed scroll 140. The eccentric crank pin 120 applies a driving force to the bushing 130. The radial component of the driving force is equal to the driving force × sinα1. The contact force is proportional to the radial component of the driving force. When L1 is greater than H1, α1 > 0, and the radial component of the driving force is positive. Therefore, the moving scroll 150 will apply a larger contact force to the fixed scroll 140, thereby increasing the power consumed by the moving scroll 150 and facilitating the rapid shutdown of the motor 170.

[0072] like Figure 5 As shown, when motor 170 reverses, the contact force between the moving scroll 150 and the fixed scroll 140 is equal to the centrifugal force of the moving scroll 150 plus the radial component of the driving force F1, F2, minus the radial gas force. The driving force F1 is the force applied to the bushing 130 by the eccentric crank pin 120. The radial component F2 indirectly reflects the radial force on the moving scroll 150. The radial gas force is the reaction force applied to the moving scroll 150 by the refrigerant. The formula shows that the larger the radial component F2, the greater the contact force between the moving scroll 150 and the fixed scroll 140. When α1 > 0, the radial component F2 is positive, thus increasing the contact force between the moving scroll 150 and the fixed scroll 140. α1 is the reverse driving angle; the larger the reverse driving angle, the greater the contact force between the moving scroll 150 and the fixed scroll 140.

[0073] Figure 5 In the diagram, line A1 is parallel to the first driving surface 121. The angle between line A1 and the radial component of force F2 is α1. The radial component of force F2 is more inclined toward the first driving surface 121 than line A1. Therefore, the angle α1 is a positive value.

[0074] When rotating in the reverse direction, the distance L1 from the center of the drive shaft 110 to the first drive surface 121 is greater than the distance H1 from the center of the unloading bushing 130 to the first driven surface 132, giving the compressor a larger reverse drive angle α1.

[0075] Combination Figure 2 and Figure 6 As shown, in some embodiments, optionally, the second drive angle is set to α2, and the eccentricity D of the scroll compressor is α2 = arcsin[(L2-H2) / D].

[0076] The eccentricity of the scroll compressor is the distance between the axis of the drive shaft 110 and the axis of the bushing 130. During the forward rotation of the motor 170, there is a contact force between the moving scroll 150 and the fixed scroll 140. The eccentric crank pin 120 applies a driving force to the bushing 130. The radial component of the driving force is equal to the driving force × sinα2. The contact force is proportional to the radial component of the driving force. When L2 is greater than H2, α2 > 0, and the radial component of the driving force is positive. Therefore, the moving scroll 150 will apply a larger contact force to the fixed scroll 140, improving the fit between the moving scroll 150 and the fixed scroll 140.

[0077] To ensure the compressor operates normally, the forward drive angle α2 is typically greater than 0, and the distance L2 from the center of the drive shaft 110 to the second drive surface 122 is greater than the distance H2 from the center of the unloading bushing 130 to the second driven surface 133. Under these conditions, the effective forward rotation drive angle α2 is greater than 0, and the direction of the driving force is the same as the rotation direction of the moving scroll 150, allowing the sidewall of the moving scroll 150 to fit well with the sidewall of the fixed scroll 140, thus achieving a seal.

[0078] When motor 170 rotates forward, the contact force between the moving scroll 150 and the fixed scroll 140 is equal to the centrifugal force of the moving scroll 150 plus the radial component of the driving force F3, F4, minus the radial gas force. The driving force F3 is the force applied to the bushing 130 by the eccentric crank pin 120. The radial component F4 is used to indirectly reflect the radial force on the moving scroll 150. The radial gas force is the reaction force applied to the moving scroll 150 by the refrigerant. It can be seen from the formula that the larger the radial component F4 is, the larger the contact force between the moving scroll 150 and the fixed scroll 140 is. When α2 > 0, the radial component F4 is positive, thus increasing the contact force between the moving scroll 150 and the fixed scroll 140.

[0079] Figure 6 In the middle, the straight line A2 is parallel to the second driving surface 122. The straight line A2 and the radial component of the force F4 are at an angle α2. The radial component of the force F4 is more biased towards the first driving surface 122 than the straight line A2. Therefore, the angle α2 is a positive value.

[0080] In an embodiment of the present invention, an air conditioner is proposed, comprising a scroll compressor as described in the above embodiment. Therefore, the air conditioner provided by the present invention has all the beneficial effects of the scroll compressor provided in the above embodiment, which will not be repeated here.

[0081] In this invention, the term "multiple" refers to two or more unless otherwise explicitly defined. The terms "install," "connect," "link," and "fix" should be interpreted broadly. For example, "connect" can be a fixed connection, a detachable connection, or an integral connection; "link" can be a direct connection or an indirect connection through an intermediate medium. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0082] In the description of this specification, the terms "one embodiment," "some embodiments," "specific embodiment," etc., refer to a specific feature, structure, material, or characteristic described in connection with that embodiment or example, which is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0083] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A scroll compressor, characterized in that, include: Drive shaft; An eccentric crank pin is provided at the end of the drive shaft. The eccentric crank pin is eccentrically arranged relative to the drive shaft, and a first driving surface is provided on the eccentric crank pin. The bushing has a mounting hole, into which the eccentric crank pin is inserted. The mounting hole has a first driven surface, which is used to push the first driven surface when the drive shaft reverses. Wherein, along the radial direction of the drive shaft, the distance between the axis of the drive shaft and the first drive surface is L1, and the distance between the axis of the bushing and the first driven surface is H1, and L1 and H1 satisfy L1 > H1.

2. The scroll compressor according to claim 1, characterized in that, The eccentric crank pin is also provided with a second driving surface, and the mounting hole is also provided with a second driven surface. When the drive shaft rotates in the forward direction, the second driving surface is used to push the second driven surface. Wherein, along the radial direction of the drive shaft, the distance between the axis of the drive shaft and the second drive surface is L2, and the distance between the axis of the bushing and the second driven surface is H2, and L2 and H2 satisfy L2 > H2.

3. The scroll compressor according to claim 2, characterized in that, There is an angle between the first driving surface and the second driving surface.

4. The scroll compressor according to claim 2, characterized in that, When the drive shaft rotates forward, the second drive surface and the second driven surface are in contact; When the drive shaft reverses, the first drive surface and the first driven surface come into contact.

5. The scroll compressor according to claim 2, characterized in that, When the drive shaft rotates in the forward direction, the second drive surface and the second driven surface separate. When the drive shaft reverses, the first drive surface and the first driven surface separate.

6. The scroll compressor according to any one of claims 2 to 5, characterized in that, A first arc-shaped surface is provided between the first side of the first driving surface and the second driving surface; A second arc-shaped surface is provided between the second side of the first driving surface and the second driving surface, and the first arc-shaped surface and the second arc-shaped surface are concentrically arranged.

7. The scroll compressor according to claim 6, characterized in that, Both the first arc-shaped surface and the second arc-shaped surface are spaced apart from the inner wall of the mounting hole.

8. The scroll compressor according to any one of claims 1 to 5, characterized in that, Let the first driving angle be α1, and the eccentricity of the scroll compressor be D, where α1 = arcsin[(L1-H1) / D].

9. The scroll compressor according to any one of claims 2 to 5, characterized in that, The second driving angle is set as α2, and the eccentricity of the scroll compressor is D, α2=arcsin[(L2-H2) / D].

10. An air conditioner, characterized in that, include: The scroll compressor as described in any one of claims 1 to 9.

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