Scroll compressor and air conditioner

Abstract

The utility model 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] The utility model belongs to the technical field of compressors, and in particular relates to a scroll compressor and an air conditioner. Background Art

[0002] When a single-phase scroll compressor is restored to power within a very short time after being disconnected from the power source, the compressor will reverse. During the reversal period, there will be no refrigerant circulation in the compressor, resulting in the air conditioner not cooling. Long-term reversal will also affect the reliability of the compressor. Utility Model Content

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

[0004] In view of this, in the first aspect, the present invention proposes a scroll compressor, comprising: a drive shaft; an eccentric crank pin, which is arranged at the end of the drive shaft, the eccentric crank pin is eccentrically arranged relative to the drive shaft, and the eccentric crank pin is provided with a first driving surface; a bushing, which is provided with a mounting hole, the eccentric crank pin is inserted into the mounting hole, and the mounting hole is provided with a first driven surface, and when the drive shaft is reversed, the first driving surface is used to push the first driven surface; 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, and the distance between the axis of the bushing and the first driven surface is H1, and L1 and H1 satisfy that L1>H1.

[0005] The scroll compressor provided by the present invention has an eccentric crank pin arranged on a drive shaft, and 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 be assembled with the movable scroll in the scroll compressor, so that the bushing can drive the movable scroll to move. The movable scroll and the fixed scroll in the scroll compressor are used to compress the refrigerant.

[0006] In a single-phase scroll compressor, under certain abnormal circumstances, such as a sudden power outage followed by a brief restoration, the compressor motor can reverse. This causes the motor to drive the drive shaft and eccentric crankpin in the opposite direction. The first driving surface of the eccentric crankpin engages the first driven surface of the unloading bushing, allowing the eccentric crankpin to drive the unloading bushing in the opposite direction.

[0007] In the above situation, reverse rotation of the motor-driven compressor is an abnormal condition. The compressor does not compress the refrigerant, causing the air conditioning system to fail to cool. When this occurs, minimal refrigerant circulates within the compressor, insufficient to cool the motor. This typically requires the motor to heat up to the protector's activation temperature, triggering the protector and stopping the motor before reversal can be stopped. The motor then cools naturally, dropping to the protector's shutdown temperature, allowing the compressor to restart normally.

[0008] When the compressor rotates in the reverse direction, the orbiting and fixed scrolls switch from compressing gas to expanding gas, effectively creating a vacuum inside the scrolls. When a compressor experiences an abnormal reverse rotation, it typically takes about an hour from reverse rotation to shutdown and restart. Prolonged cooling failures can lead to user complaints. Prolonged reverse operation can also cause wear and tear on components.

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

[0010] Specifically, the greater the radial interaction force between the movable scroll and the fixed scroll, the better the sealing effect between the movable scroll and the fixed scroll. When the distance between the axis of the drive shaft and the first drive surface is greater than the distance between the axis of the bushing and the first driven surface, the radial component of the force applied to the movable scroll is larger, thereby increasing the contact force between the movable scroll and the fixed scroll. The greater the force applied by the movable scroll to the fixed scroll, the more power the movable scroll consumes. At this time, the current of the motor is larger, the heat generated by the motor increases, the heating rate is accelerated, the time it takes for the motor to heat up to the protector opening temperature is shorter, and the time required for the compressor to reverse, stop, and restart is shorter, avoiding the problem of the air-conditioning system being unable to cool for a long time, reducing the wear of components, and helping to improve the reliability of the compressor.

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

[0012] In some technical solutions, optionally, a second driving surface is provided on the eccentric crank pin, and a second driven surface is provided in the mounting hole. When the drive shaft rotates forward, 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 driving 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.

[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 force on the orbiting scroll is greater during forward rotation of the motor, thereby increasing the contact force between the orbiting scroll and the fixed scroll. The greater the force exerted by the orbiting scroll on the fixed scroll, the better the sealing between the orbiting 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 angle between the first driving surface and the second driving surface.

[0015] The first and second drive surfaces of the eccentric crankpin are angled, meaning they are non-parallel. This ensures the compressor maintains both adequate radial sealing force and a strong radial sealing force during reverse rotation. This allows for a higher operating current during reverse rotation in certain abnormal situations, prompting 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 with each other; when the drive shaft rotates reversely, the first driving surface and the first driven surface are in contact with each other.

[0017] When the compressor rotates forward, the drive shaft rotates forward. During this process, the second driving surface pushes the second driven surface. In this solution, the second driving surface and the second driven surface fit together, that is, the second driving surface and the second driven surface are parallel to each other, so that the second driving surface and the second driven surface can fit closely together, and the two have a large contact area, which is beneficial to improving the driving stability of the eccentric crank pin to the bushing.

[0018] Similarly, when the compressor reverses, the drive shaft reverses. During this process, the first driving surface pushes the first driven surface. In this solution, the first driving surface and the first driven surface fit together, that is, the first driving surface and the first driven surface are parallel to each other, so that the first driving surface and the first driven surface can fit closely together, and the two have a larger 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 are separated; when the drive shaft rotates reversely, the first driving surface and the first driven surface are separated.

[0021] When the drive shaft reverses, the first driving surface and the first driven surface are in contact, so that the first driving surface can push the first driven surface. At this time, the second driving surface and the second driven surface are separated, avoiding the second driving surface and the second driven surface from interfering with each other and affecting the force applied to the movable 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, so that the second driving surface can push the second driven surface. At this time, the first driving surface and the first driven surface are separated, avoiding the first driving surface and the first driven surface from interfering with each other and affecting the force applied to the movable scroll when the motor rotates forward.

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

[0024] The two sides of the first driving surface are connected to the second driving surface through arc surfaces respectively. The arc surfaces on both sides of the first driving surface are concentrically arranged, that is, the axis of the first arc surface and the axis of the second arc surface are collinear, and there is no need to design the axis of the first arc surface and the second arc surface separately, which is conducive to reducing the processing difficulty of the eccentric crank pin.

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

[0026] Neither the first curved surface nor the second curved surface fits the inner wall of the mounting hole. During the forward or reverse rotation of the drive shaft, the first curved surface and the second curved surface will not come into contact with the inner wall of the mounting hole, thereby avoiding interference between the first curved surface and the second curved surface and the inner wall of the mounting hole, and preventing the force applied to the movable scroll when the motor rotates.

[0027] In some technical solutions, optionally, the first driving angle is set to α1, the eccentricity of the scroll compressor is D, and 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 reversal of the motor, there is a contact force between the movable scroll and the fixed scroll. The eccentric crank pin applies a driving force to the bushing. The radial component of the driving force = driving force × sin α1. 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 movable scroll will exert a greater contact force than the given scroll, thereby increasing the power consumed by the movable scroll, which is conducive to achieving rapid shutdown of the motor.

[0029] In some technical solutions, optionally, the second driving angle is set to α2, the eccentricity of the scroll compressor is D, and 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 movable scroll and the fixed scroll. The eccentric crank pin applies a driving force to the bushing. The radial component of the driving force = 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 movable scroll will exert a greater contact force than the fixed scroll, thereby improving the fitting effect between the movable scroll and the fixed scroll.

[0031] In a second aspect, the present invention proposes an air conditioner, comprising: a scroll compressor as 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 present invention will become apparent in the following description or will be understood through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[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 in conjunction with the following drawings, in which:

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

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

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

[0037] Figure 4 A schematic structural diagram of a bushing in an embodiment of the present utility model is shown;

[0038] Figure 5 A schematic diagram showing the cooperation between the eccentric crank pin and the bushing when the motor is reversed in an embodiment of the present utility model is shown;

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

[0040] Figure 7 The structure diagram of the scroll compressor in the embodiment of the present utility model is shown.

[0041] Reference numerals:

[0042] 100 scroll compressor, 110 drive shaft, 120 eccentric crank pin, 121 first drive surface, 122 second drive surface, 123 first arcuate surface, 124 second arcuate surface, 130 bushing, 131 mounting hole, 132 first driven surface, 133 second driven surface, 140 fixed scroll, 150 orbiting scroll, 160 bearing seat, 170 motor, 180 frame. DETAILED DESCRIPTION

[0043] In order to more clearly understand the above-mentioned objectives, features and advantages of the present invention, the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments. It should be noted that the embodiments of the present application and the features therein can be combined with each other without conflict.

[0044] In the following description, many specific details are set forth to facilitate a full understanding of the present invention. However, the present invention may also be implemented in other ways different from those described herein. Therefore, the scope of protection of the present invention is not limited to the specific embodiments disclosed below.

[0045] Refer to the following Figures 1 to 7 The present invention will now be described in detail with reference to a scroll compressor and an air conditioner according to some embodiments of the present invention.

[0046] Combine 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 proposed, comprising: a drive shaft 110, an eccentric crank pin 120 and a bushing 130. The eccentric crank pin 120 is provided at the end of the drive shaft 110. The eccentric crank pin 120 is eccentrically arranged relative to the drive shaft 110. The eccentric crank pin 120 is provided with a first driving surface 121. The bushing 130 is provided with a mounting hole 131. The eccentric crank pin 120 is inserted into the mounting hole 131. The mounting hole 131 is provided with a first driven surface 132. When the drive shaft 110 is reversed, 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 R in the figure points to the axis of the drive shaft 110 ( Figure 2 The arrow at the mark O1 points to the axis of the drive shaft 110 and the distance between the first drive surface 121 is L1, and the axis of the bushing 130 ( Figure 2 The arrow at the position marked O2 points to the axis of the bushing 130 , and the distance between the position and the first driven surface 132 is H1 , and L1 and H1 satisfy L1>H1.

[0047] The scroll compressor 100 provided by the present invention has an eccentric crank pin 120 arranged 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 be assembled with the movable scroll 150 in the scroll compressor 100, so that the bushing 130 can drive the movable scroll 150 to move. The movable scroll 150 and the fixed scroll 140 in the scroll compressor 100 are used to compress the refrigerant.

[0048] In a single-phase scroll compressor 100, under certain abnormal circumstances, such as a sudden power outage followed by a very short power restoration, the compressor motor 170 may reverse. The motor 170 then 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. This structure allows the eccentric crank pin 120 to drive the unloading bushing 130 to rotate in the opposite direction.

[0049] In the above situation, reverse rotation of the compressor driven by motor 170 is an abnormal condition. The compressor does not compress the refrigerant, causing the air conditioning system to fail to cool. When this occurs, minimal refrigerant circulates within the compressor, insufficient to cool motor 170. This typically requires motor 170 to heat up to the protector's activation temperature, triggering the protector and stopping motor 170 before reverse rotation can be stopped. Subsequently, motor 170 cools naturally, dropping to the protector's shutdown temperature, allowing the compressor to restart normally.

[0050] When the compressor rotates in the reverse direction, the compressed gas in the orbiting scroll 150 and the fixed scroll 140 is converted to expanded gas, effectively creating a vacuum inside the scrolls. When a compressor experiences an abnormal reverse rotation, it typically takes about an hour for the system to shut down and restart. Prolonged cooling failures can lead to user complaints. Prolonged reverse operation can also cause wear and tear on components.

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

[0052] Specifically, the greater the radial interaction force between the orbiting scroll 150 and the fixed scroll 140, the better the sealing effect between the orbiting scroll 150 and the fixed scroll 140. 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 orbiting scroll 150 is greater, thereby increasing the contact force between the orbiting scroll 150 and the fixed scroll 140. The greater the force applied by the orbiting scroll 150 to the fixed scroll 140, the greater the power consumed by the orbiting scroll 150. At this time, the current of the motor 170 is greater, the heat generated by the motor 170 increases, the heating rate is accelerated, the time it takes for the motor 170 to heat up to the protector opening temperature is shorter, and the time required for the compressor to reverse, stop, and restart is shorter. This avoids the problem of the air conditioning system being unable to cool for a long time, reduces the wear of components, and is conducive to 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 direction of rotation of the orbiting scroll 150. This prevents the sidewalls of the orbiting scroll 150 from properly fitting with the sidewalls of the fixed scroll 140, resulting in significant radial leakage. Therefore, when the compressor rotates in reverse, the current is typically low, the motor 170 generates less heat and heats up more slowly, and it takes a long time for the motor 170 to reach the protector opening temperature. This embodiment addresses this issue by setting the relationship between L1 and H1.

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

[0055] In some embodiments, optionally, a second driving surface 122 is further provided on the eccentric crank pin 120, and a second driven surface 133 is further provided in the mounting hole 131. When the drive shaft 110 rotates forward, the second driving surface 122 is configured 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 orbiting scroll 150 is greater during forward rotation of the motor 170, thereby increasing the contact force between the orbiting scroll 150 and the fixed scroll 140. The greater the force exerted by the orbiting scroll 150 on the fixed scroll 140, the better the sealing between the orbiting scroll 150 and the fixed scroll 140, thus avoiding refrigerant leakage and improving the performance of the scroll compressor 100.

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

[0058] The first drive surface 121 and the second drive surface 122 of the eccentric crank pin 120 form an included angle β. That is, the eccentric crank pin 120 has a first drive surface 121 and a second drive surface 122 that are non-parallel to each other. This ensures that the compressor has both appropriate radial sealing force and a strong radial sealing force during reverse rotation. This allows the compressor to draw a higher operating current during reverse rotation under certain abnormal circumstances, allowing the compressor protector to activate more quickly and improving compressor reliability.

[0059] Combine 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 with each other, and when the drive shaft 110 rotates reversely, the first drive surface 121 and the first driven surface 132 are in contact with each other.

[0060] When the compressor rotates forward, the drive shaft 110 rotates forward. During this process, the second driving surface 122 pushes the second driven surface 133. In this solution, the second driving surface 122 and the second driven surface 133 fit together, that is, the second driving surface 122 and the second driven surface 133 are parallel to each other, so that the second driving surface 122 and the second driven surface 133 can fit closely together, and 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.

[0061] Similarly, when the compressor reverses, the drive shaft 110 reverses. During this process, the first driving surface 121 pushes the first driven surface 132. In this solution, the first driving surface 121 and the first driven surface 132 fit together, that is, the first driving surface 121 and the first driven surface 132 are parallel to each other, so that the first driving surface 121 and the first driven surface 132 can fit closely together, and the two have a larger 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] Combine 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 separated. When the drive shaft 110 rotates reversely, the first drive surface 121 and the first driven surface 132 are separated.

[0064] When the drive shaft 110 reverses, the first driving surface 121 and the first driven surface 132 fit together, so that the first driving surface 121 can push the first driven surface 132. At this time, the second driving surface 122 and the second driven surface 133 are separated, avoiding the second driving surface 122 and the second driven surface 133 from interfering with each other and affecting the force applied to the movable 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 fit together, 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, avoiding the first drive surface 121 and the first driven surface 132 from interfering with each other and affecting the force applied to the movable 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 surfaces respectively. The arc surfaces on both sides of the first driving surface 121 are concentrically arranged, that is, the axis of the first arc surface 123 and the axis of the second arc surface 124 are collinear, and there is no need to design the axis for the first arc surface 123 and the second arc surface 124 respectively, which is beneficial to reducing the processing difficulty of the eccentric crank pin 120.

[0068] Combine 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 curved surface 123 nor the second curved surface 124 fits the inner wall of the mounting hole 131. During the forward or reverse rotation of the drive shaft 110, the first curved surface 123 and the second curved surface 124 will not come into contact with the inner wall of the mounting hole 131, thereby avoiding interference between the first curved surface 123 and the second curved surface 124 and the inner wall of the mounting hole 131, thereby preventing the force applied to the movable scroll 150 when the motor 170 rotates.

[0070] Combine Figure 2 and Figure 6 As shown, in some embodiments, optionally, the first driving angle is set to α1, the eccentricity of the scroll compressor is D, and 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 reversal of the motor 170, there is a contact force between the movable 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 = driving force × sin α1. 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 movable scroll 150 will exert a greater contact force on the given scroll 140, thereby increasing the power consumed by the movable scroll 150, which is conducive to achieving rapid shutdown of the motor 170.

[0072] like Figure 5 As shown, when the motor 170 rotates reversely, the contact force between the orbiting scroll 150 and the fixed scroll 140 = the centrifugal force of the orbiting scroll 150 + the radial component F2 of the driving force F1 - the radial gas force. The driving force F1 is the force applied to the bushing 130 by the eccentric crankpin 120. The radial component F2 indirectly reflects the radial force on the orbiting scroll 150. The radial gas force is the reaction force applied to the orbiting scroll 150 by the refrigerant. The formula shows that the greater the radial component F2, the greater the contact force between the orbiting scroll 150 and the fixed scroll 140. When α1 > 0, the radial component F2 is positive, thereby increasing the contact force between the orbiting scroll 150 and the fixed scroll 140. α1 is the reverse drive angle. A larger reverse drive angle increases the contact force between the orbiting scroll 150 and the fixed scroll 140.

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

[0074] During reverse rotation, the distance L1 from the center of the drive shaft 110 to the first driving surface 121 is greater than the distance H1 from the center of the unloading bushing 130 to the first driven surface 132 , so that the compressor has a larger reverse driving angle α1 .

[0075] Combine Figure 2 and Figure 6 As shown, in some embodiments, optionally, the second driving angle is set to α2, the eccentricity D of the scroll compressor, 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 movable 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 = driving force × sin α2. 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 movable scroll 150 will exert a greater contact force than the fixed scroll 140, thereby improving the fitting effect between the movable scroll 150 and the fixed scroll 140.

[0077] Typically, to ensure that the forward drive angle α2 is greater than 0 during normal operation of the compressor, 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. In this case, the effective forward drive angle α2 is greater than 0, and the direction of the driving force is the same as the rotation direction of the orbiting scroll 150, allowing the sidewalls of the orbiting scroll 150 to fit well with the sidewalls of the fixed scroll 140, thereby achieving a seal.

[0078] When the motor 170 rotates forward, the contact force between the movable scroll 150 and the fixed scroll 140 = the centrifugal force of the movable scroll 150 + the radial component F4 of the driving force F3 - the radial gas force, where the driving force F3 is the force applied by the eccentric crank pin 120 to the bushing 130, and the radial component F4 is used to indirectly reflect the radial force on the movable scroll 150. The radial gas force is the reaction force applied by the refrigerant to the movable scroll 150. It can be seen from the formula that the greater the radial component F4, the greater the contact force between the movable scroll 150 and the fixed scroll 140. When α2>0, the radial component F4 is a positive value, and therefore, the contact force between the movable scroll 150 and the fixed scroll 140 will increase.

[0079] Figure 6 In the figure, the straight line A2 is parallel to the second driving surface 122 , and an angle α2 is formed between the straight line A2 and the radial component force F4 . The radial component force F4 is more inclined toward the first driving surface 122 than the straight line A2 . Therefore, the angle α2 is a positive value.

[0080] In the embodiment of the present invention, an air conditioner is proposed, including: a scroll compressor as 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 utility model, the term "plurality" refers to two or more, unless otherwise specified. Terms such as "installed," "connected," "connected," and "fixed" should be interpreted broadly. For example, "connected" can mean fixed, removable, or integral; "connected" can mean directly or indirectly through an intermediary. Those skilled in the art will understand the specific meanings of these terms in this utility model based on specific circumstances.

[0082] Throughout this specification, terms such as "one embodiment," "some embodiments," and "specific embodiments" mean that the specific features, structures, materials, or characteristics described in conjunction with that embodiment or example are included in at least one embodiment or example of the present invention. In this specification, schematic representations of these 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 any 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 present invention. Those skilled in the art will readily appreciate that the present invention is susceptible to various modifications and variations. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention shall 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, disposed at an end of the drive shaft, the eccentric crank pin being eccentrically disposed relative to the drive shaft, and having a first driving surface disposed on the eccentric crank pin; A bushing is provided with a mounting hole, the eccentric crank pin is inserted into the mounting hole, a first driven surface is provided in the mounting hole, and when the drive shaft is reversed, the first driving surface is used to push the first driven surface; In 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, wherein: The eccentric crank pin is further provided with a second driving surface, and the mounting hole is further provided with a second driven surface. When the drive shaft rotates forward, the second driving surface is used to push the second driven surface. In 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. L2 and H2 satisfy L2>H2.

3. The scroll compressor according to claim 2, wherein: There is an included angle between the first driving surface and the second driving surface.

4. The scroll compressor according to claim 2, wherein: When the drive shaft rotates forward, the second driving surface and the second driven surface are in contact with each other; When the drive shaft is reversed, the first driving surface and the first driven surface come into contact with each other.

5. The scroll compressor according to claim 2, wherein: When the drive shaft rotates forward, the second driving surface and the second driven surface are separated; When the drive shaft is reversed, the first driving surface and the first driven surface are separated.

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

7. The scroll compressor according to claim 6, characterized in that The first arcuate surface and the second arcuate surface are both 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: The first driving angle is set to α1, the eccentricity of the scroll compressor is D, and 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 to α2, the eccentricity of the scroll compressor is D, and α2=arcsin[(L2-H2) / D].

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

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