A scroll compressor, air conditioner and automobile

Abstract

This invention provides a scroll compressor, an air conditioner, and an automobile, which solves the technical problem in the prior art that the pressure of the back pressure chamber cannot be adjusted according to the crankshaft rotation speed. It includes a stationary disc, a moving disc, a crankshaft, and a bracket. The stationary disc is fixed on the bracket, and the moving disc is located between the stationary disc and the bracket. A compression chamber is formed between the stationary disc and the moving disc, and a back pressure chamber is formed between the moving disc and the bracket. A low-pressure chamber is provided on the side of the bracket facing away from the back pressure chamber. A first end of the crankshaft passes through the bracket and is connected to the moving disc, and a second end of the crankshaft is located on the side of the bracket facing away from the back pressure chamber. The scroll compressor is provided with a pressure regulating passage, which sequentially connects the compression chamber, the back pressure chamber, and the low-pressure chamber. A pressure regulating device is provided on the pressure regulating passage, which can adjust the pressure of the back pressure chamber according to the crankshaft rotation speed.

Description

Technical Field

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

[0002] With increasing global emphasis on energy conservation and environmental protection, electric vehicles are gradually becoming the future direction of automotive development. Consequently, scroll compressors for electric vehicle air conditioning have become a key area of ​​research and development. When an electric scroll compressor operates, the moving scroll plate is affected by axial gas force, resulting in axial clearance and radial leakage. Therefore, existing electric scroll compressors employ a unique back pressure chamber to provide back pressure to balance the axial gas force. Insufficient back pressure leads to axial clearance and internal leakage within the compressor; excessive back pressure accelerates wear on the moving and stationary scroll plates. Therefore, a dynamic balance between back pressure and axial force is necessary to improve the compressor's performance and reliability.

[0003] In existing technology, the compression chamber and the back pressure chamber are connected by a channel, allowing the gas in the back pressure chamber to communicate with the gas in the compression chamber. For compressors equipped with control valves, the pressure in the compression chamber is stable, and the pressure in the back pressure chamber is also non-adjustable and stable. Thus, when the rotating disc rotates at a high speed, the vibration of the rotating disc increases, and the pressure in the back pressure chamber cannot be increased to suppress the large vibration generated by the rotating disc, nor can the axial clearance between the rotating disc and the stationary disc be eliminated. Similarly, when the rotating disc rotates at a low speed, the vibration of the rotating disc is small, and the pressure in the back pressure chamber cannot be reduced to reduce the axial friction between the rotating disc and the stationary disc. Summary of the Invention

[0004] Therefore, the present invention provides a scroll compressor, an air conditioner, and an automobile that can solve the technical problem in the prior art that the pressure of the back pressure chamber cannot be adjusted according to the crankshaft speed.

[0005] In a first aspect, the present invention provides a scroll compressor, comprising a stationary disc, a moving disc, a crankshaft, and a bracket. The stationary disc is fixed on the bracket, the moving disc is located between the stationary disc and the bracket, a compression cavity is formed between the stationary disc and the moving disc, a back pressure cavity is formed between the moving disc and the bracket, and a low pressure cavity is provided on the side of the bracket facing away from the back pressure cavity. A first end of the crankshaft passes through the bracket and is connected to the moving disc, and a second end of the crankshaft is located on the side of the bracket facing away from the back pressure cavity.

[0006] The scroll compressor is provided with a pressure regulating passage, which is connected in sequence to the compression chamber, the back pressure chamber and the low pressure chamber; a pressure regulating device is provided on the pressure regulating passage, which can adjust the pressure of the back pressure chamber according to the rotational speed of the crankshaft.

[0007] In some embodiments, the pressure regulating device includes a slider, and the pressure regulating passage includes a pressure regulating section; the slider is at least partially disposed within the pressure regulating section, and the rotation of the crankshaft enables the slider to move within the pressure regulating section; the sliding of the slider within the pressure regulating passage can change the pressure on both sides of the slider's movement direction, and the pressure difference on both sides of the slider's movement direction is negatively correlated with the crankshaft's rotational speed.

[0008] In some embodiments, the pressure regulating device further includes an elastic element, the movement of which can cause the elastic element to deform.

[0009] In some embodiments, the pressure regulating section includes a removable inner sleeve, and the slider is at least partially disposed within the inner sleeve.

[0010] In some embodiments, the inner sleeve is a first housing, the inner hole of the first housing is a tapered hole, and the small end of the tapered hole faces the air intake direction of the tapered hole;

[0011] The slider is a first slider and is capable of moving within the tapered hole along the axial direction of the tapered hole.

[0012] In some embodiments, the first slider includes an outer surface opposite to the inner surface of the tapered hole, and the outer surface of the first slider is a cylindrical surface; or, the outer surface of the first slider is a conical surface, and the small end of the conical surface is in the same direction as the small end of the tapered hole.

[0013] In some embodiments, the elastic element is a spring, the spring including a first spring and a second spring, and the first slider includes a first end facing the small end of the tapered hole and a second end opposite to the first end of the first slider;

[0014] One end of the first spring is connected to the first end of the first slider, and the other end of the first spring is connected to the inner sleeve. One end of the second spring is connected to the second end of the first slider, and the other end of the second spring is connected to the inner sleeve.

[0015] In some embodiments, the pressure regulating device further includes a support rod, one end of which faces the small end of the tapered hole and the other end of which faces the large end of the tapered hole; the first slider is movably disposed on the support rod.

[0016] In some embodiments, the inner sleeve is a second housing, the inner hole of the second housing is a sliding hole, the slider is a second slider, the outer surface of the second slider is slidably attached to the inner wall surface of the sliding hole; the outer surface of the second slider is provided with a first groove, the inlet end of the first groove is close to the rotation axis of the crankshaft, and the outlet end of the first groove is far away from the rotation axis of the crankshaft;

[0017] The second slider is at least partially able to slide out of the sliding hole.

[0018] In some embodiments, the outer surface of the second slider is a cylindrical surface, and the first groove is a spiral groove surrounding the outer surface of the second slider.

[0019] In some embodiments, a baffle is provided at one end of the inner sleeve away from the rotation axis of the crankshaft, and a vent hole is provided on the baffle; the baffle is fixed to the inner sleeve by a plurality of connectors, and a gap is formed between two adjacent connectors.

[0020] In some embodiments, the elastic element is a third spring, the inner sleeve is provided with an inner cavity having an opening away from the axis of rotation of the crankshaft, and the third spring is disposed in the inner cavity and located between the second slider and the baffle.

[0021] In some embodiments, a first air inlet channel is provided between the compression chamber and the back pressure chamber, connecting the compression chamber and the back pressure chamber; a first air outlet channel is provided between the back pressure chamber and the low pressure chamber, connecting the back pressure chamber and the low pressure chamber; the pressure regulating device is disposed in the first air outlet channel.

[0022] In some embodiments, an eccentric sleeve is provided between the first end of the crankshaft and the moving disk, the eccentric sleeve including a first end face facing the moving disk and a second end face opposite to the first end face; an air gap is formed between the first end face of the eccentric sleeve and the moving disk; a first channel communicating between the compression chamber and the air gap is provided on the moving disk;

[0023] The eccentric sleeve includes a journal extending toward the moving disk, a first bearing is sleeved on the journal, the inner ring of the first bearing is connected to the journal, the outer ring of the first bearing is connected to the moving disk, a first gap is formed between the inner ring and the outer ring of the first bearing, and the first gap connects the air gap and the back pressure chamber.

[0024] In some embodiments, a second groove is formed between the second end face of the eccentric sleeve and the first end face of the crankshaft, and a second channel and a third channel are provided on the crankshaft;

[0025] The outlet of the third channel faces the low-pressure chamber; one end of the second channel is connected to the third channel, and the other end is connected to the second groove; the second groove is connected to the back pressure chamber; the pressure regulating device is disposed in the third channel.

[0026] In some embodiments, the centerline of the second channel coincides with the axis of the crankshaft; there are multiple third channels, which are evenly distributed along the circumference of the crankshaft, and the inlets of the multiple third channels are connected to the outlet of the second channel.

[0027] In some embodiments, a second air inlet channel is provided between the compression chamber and the back pressure chamber, connecting the compression chamber and the back pressure chamber; a second air outlet channel is provided between the back pressure chamber and the low pressure chamber, connecting the back pressure chamber and the low pressure chamber; the pressure regulating device is disposed in the second air inlet channel.

[0028] In some embodiments, an eccentric sleeve is provided between the first end of the crankshaft and the moving disk;

[0029] The second intake passage includes a first flow channel connected end to end and disposed on the moving plate, a second flow channel disposed on the eccentric sleeve, a third flow channel disposed on the crankshaft, and a fourth flow channel disposed on the crankshaft; the fourth flow channel leads to the back pressure chamber, and the pressure regulating device is disposed in the fourth flow channel.

[0030] In some embodiments, the eccentric sleeve and the crankshaft are connected by a crank pin, with one end of the crank pin inserted into the eccentric sleeve and the other end inserted into the crankshaft;

[0031] The crank pin is provided with a fifth flow channel, one end of which is connected to the second flow channel and the other end of which is connected to the third flow channel.

[0032] In some embodiments, the centerline of the third flow channel coincides with the axis of the crankshaft; there are multiple fourth flow channels, which are evenly distributed along the circumference of the crankshaft, and the inlets of the multiple fourth flow channels are connected to the outlet of the third flow channel.

[0033] In some embodiments, the bracket is provided with a shaft hole, and the crankshaft passes through the shaft hole;

[0034] The inner wall of the shaft hole is provided with an annular groove surrounding the crankshaft, and a sealing part is provided between the annular groove and the low-pressure chamber; a second bearing for supporting the crankshaft is also provided between the shaft hole and the back pressure chamber, the second bearing includes a first inner ring and a second outer ring, and a second gap is formed between the first inner ring and the second outer ring; the second gap connects the back pressure chamber and the annular groove, and the outlet of the fourth flow channel faces the annular groove.

[0035] Secondly, the present invention also provides an air conditioner, including the aforementioned scroll compressor.

[0036] Thirdly, the present invention provides an automobile including the aforementioned air conditioner.

[0037] This invention provides a pressure regulating device in the pressure regulating path that flows through the compression chamber, back pressure chamber, and low pressure chamber. This device can adjust the pressure in the back pressure chamber according to the crankshaft speed, thereby making the pressure in the back pressure chamber related to the crankshaft speed (the speed of the moving disc), thus improving the stability of the scroll compressor. Attached Figure Description

[0038] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0039] Figure 1 This is a schematic diagram of the pressure regulating device being installed on the first outlet channel according to an embodiment of the present invention;

[0040] Figure 2 This is an embodiment of the present invention. Figure 1 Enlarged view of point A in the middle;

[0041] Figure 3 This is a schematic diagram of the pressure regulating device being installed on the second intake channel according to an embodiment of the present invention;

[0042] Figure 4 This is an embodiment of the present invention. Figure 3 Enlarged view at point B in the middle;

[0043] Figure 5 This is an embodiment of the present invention. Figure 3 Enlarged view at point C;

[0044] Figure 6 This is a schematic diagram of the first spring in a compressed state according to an embodiment of the present invention;

[0045] Figure 7 This is a schematic diagram of the second spring in a compressed state according to an embodiment of the present invention;

[0046] Figure 8 This is a schematic diagram of the first slider in an embodiment of the present invention having a conical outer surface;

[0047] Figure 9 This is a schematic diagram of two first shells combined into a first long shell according to an embodiment of the present invention;

[0048] Figure 10 This is a perspective view of the second housing, the second slider, and the third spring assembled in an embodiment of the present invention.

[0049] Figure 11 This is a schematic diagram of the baffle in an embodiment of the present invention;

[0050] Figure 12 This is a schematic diagram of the second slider inside the second housing when the crankshaft speed is low, according to an embodiment of the present invention.

[0051] Figure 13 This is a schematic diagram of the second slider inside the second housing when the crankshaft speed is high, according to an embodiment of the present invention.

[0052] The reference numerals in the attached figures are as follows:

[0053] 101. Stationary disc; 102. Crank pin; 103. Bracket; 1031. Annular groove; 201. Moving disc; 202. Crankshaft; 3. Compression chamber; 301. First bearing; 3011. First spacer; 4. Back pressure chamber; 401. Second bearing; 4011. Second spacer; 5. Low pressure chamber; 6. Pressure regulating device; 601. First slider; 602. First spring; 603. Second spring; 604. First housing; 605. Connecting rod; 606. Baffle; 607. Vent hole 608. Third spring; 609. Third gap; 610. Support rod; 6041. First long shell; 6042. Tapered hole; 701. Second slider; 702. First groove; 704. Second shell; 711. First channel; 712. Second channel; 713. Third channel; 9. Eccentric sleeve; 901. Journal; 902. Air gap; 801. First flow channel; 802. Second flow channel; 803. Third flow channel; 804. Fourth flow channel; 805. Fifth flow channel. Detailed Implementation

[0054] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0055] It should be noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to limit the exemplary embodiments according to this application. As used herein, the singular form is intended to include the plural form as well, unless the context clearly indicates otherwise. Furthermore, it should be understood that when the terms "comprising" and / or "including" are used in this specification, they indicate the presence of features, steps, operations, devices, components, and / or combinations thereof.

[0056] It should be understood that the term "and / or" used in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, and B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0057] Unless otherwise specifically stated, the relative arrangement, numerical expressions, and values ​​of the components and steps described in these embodiments do not limit the scope of the invention. It should also be understood that, for ease of description, the structures, proportions, sizes, etc., shown in the accompanying drawings are only for the purpose of illustrative purposes and to facilitate understanding and reading by those skilled in the art, and are not intended to limit the conditions under which the invention can be implemented. Any modifications to the structure, changes in proportions, or adjustments to size, without affecting the effects and objectives achieved by the invention, should still fall within the scope of the technical content disclosed in the invention. Techniques, methods, and devices known to those skilled in the art may not be discussed in detail, but where appropriate, such techniques, methods, and devices should be considered part of the specification. In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not as limitations. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters in the following figures denote similar items; therefore, once an item is defined in one figure, it does not need to be further discussed in subsequent figures.

[0058] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0059] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatial relative descriptions used herein will be interpreted accordingly.

[0060] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0061] This invention belongs to the field of compressor technology, specifically relating to a scroll compressor, an air conditioner, and an automobile.

[0062] With increasing global emphasis on energy conservation and environmental protection, electric vehicles are gradually becoming the future direction of automotive development. Consequently, scroll compressors for electric vehicle air conditioning have become a key area of ​​research and development. When an electric scroll compressor operates, the moving scroll plate is affected by axial gas force, resulting in axial clearance and radial leakage. Therefore, existing electric scroll compressors employ a unique back pressure chamber to provide back pressure to balance the axial gas force. Insufficient back pressure leads to axial clearance and internal leakage within the compressor; excessive back pressure accelerates wear on the moving and stationary scroll plates. Therefore, a dynamic balance between back pressure and axial force is necessary to improve the compressor's performance and reliability.

[0063] Therefore, the present invention provides a scroll compressor, an air conditioner, and an automobile that can solve the technical problem in the prior art that the pressure of the back pressure chamber cannot be adjusted according to the crankshaft speed.

[0064] like Figure 1-13As shown, a scroll compressor includes a stationary disc 101, a moving disc 201, a crankshaft 202, and a bracket 103. The stationary disc 101 is fixed on the bracket 103, and the moving disc 201 is located between the stationary disc 101 and the bracket 103. A compression chamber 3 is formed between the stationary disc 101 and the moving disc 201, and a back pressure chamber 4 is formed between the moving disc 201 and the bracket 103. A low-pressure chamber 5 is provided on the side of the bracket 103 facing away from the back pressure chamber 4. The first end of the crankshaft 202 passes through the bracket 103 and is connected to the moving disc 201, and the second end of the crankshaft 202 is located on the side of the bracket 103 facing away from the back pressure chamber 4.

[0065] The scroll compressor is provided with a pressure regulating passage, which is connected in sequence to the compression chamber 3, the back pressure chamber 4 and the low pressure chamber 5; a pressure regulating device 6 is provided on the pressure regulating passage, which can adjust the pressure of the back pressure chamber 4 according to the rotational speed of the crankshaft 202.

[0066] A pressure regulating device 6 is installed in the pressure regulating passage to make the pressure in the back pressure chamber 4 related to the rotation of the crankshaft 202, thereby making the pressure in the back pressure chamber 4 related to the rotation speed of the crankshaft 202. This keeps the pressure in the compression chamber 3 and the back pressure chamber 4 on both sides of the moving plate 201 relatively constant, thus ensuring that the axial friction between the moving plate 201 and the stationary plate 101 is within a reasonable range and also avoiding excessive axial clearance between the moving plate 201 and the stationary plate 101, which could lead to gas leakage.

[0067] When the exhaust port of the scroll compressor is equipped with a control valve, the pressure in the compression chamber 3 is related to the control valve but not to the rotational speed of the crankshaft 202. The rotational speed of the crankshaft 202 is related to the flow rate. When the exhaust port of the scroll compressor is a throttling orifice, the pressure in the compression chamber 3 is positively correlated with the rotational speed of the crankshaft 202 (that is, the revolution speed of the moving disc 201).

[0068] The effect achieved by the pressure regulating device 6 varies depending on its location.

[0069] Scenario 1: The compressor's exhaust port is equipped with a control valve; the higher the crankshaft 202's rotational speed, the greater the pressure in the back pressure chamber 4; in this case, the pressure regulating device 6 is installed in the passage from the compression chamber 3 to the back pressure chamber 4. When the external required flow rate is large, the crankshaft 202's rotational speed increases, but the pressure in the compression chamber 3 does not increase. Due to the increased rotational speed of the moving disc 201, the vibration of the moving disc 201 also increases. At this time, the pressure regulating device 6 increases the pressure in the back pressure chamber 4 to suppress the vibration of the moving disc 201, reducing the excessive axial friction or gap between the stationary disc 101 and the moving disc 201 caused by the vibration of the moving disc 201; when the external required flow rate is small, the crankshaft 202's rotational speed decreases, but the pressure in the compression chamber 3 does not decrease. Due to the decreased rotational speed of the moving disc 201, the vibration of the moving disc 201 also decreases. At this time, the pressure regulating device 6 reduces the pressure in the back pressure chamber 4 to avoid excessive pressure in the back pressure chamber 4, which would cause excessive axial extrusion between the stationary disc 101 and the moving disc 201 and excessive magnetic friction.

[0070] Scenario 2: The compressor's discharge port is a throttling orifice. Compared to Scenario 1, the sealing requirements are lower. Scenario 2 is more suitable for high pressure ratio conditions and heavy loads. The higher the crankshaft 202 speed, the higher the pressure in the back pressure chamber 4 needs to be. However, the rate of pressure increase in the back pressure chamber 4 is less than the rate of pressure increase in the compression chamber 3. At this time, the pressure regulating device 6 is set in the passage from the back pressure chamber 4 to the low pressure chamber 5 (used to relieve pressure in the back pressure chamber 4). At this time, the pressure in the back pressure chamber 4 is approximately equal to (slightly lower than) the pressure in the compression chamber 3. When the external flow rate is large, the crankshaft 202 speed increases, and the pressure in the compression chamber 3 increases accordingly. Due to the increased rotation speed of the moving disc 201, the vibration of the moving disc 201 also increases. At this time, the pressure regulating device 6 increases the pressure in the back pressure chamber. The pressure of 4 is used to suppress the vibration of the moving plate 201 and reduce the excessive friction or gap between the stationary plate 101 and the moving plate 201 caused by the vibration of the moving plate 201. Compared with "Case 1", the pressure in the compression chamber 3 of Case 2 is larger, which makes the pressure in the back pressure chamber 4 also larger. From the actual inspection, the axial wear of the moving plate 201 and the stationary plate 101 increases at this time, that is, the pressure in the back pressure chamber 4 is too large, and it is necessary to depressurize the back pressure chamber 4. At this time, the pressure regulating device 6 reduces the pressure in the back pressure chamber 4. When the external flow rate is small, the crankshaft 202 speed decreases, and the pressure in the compression chamber 3 also decreases. From the actual situation, the pressure in the back pressure chamber 4 also decreases accordingly and decreases too much. At this time, the pressure in the back pressure chamber 4 is increased by the pressure regulating device 6.

[0071] When the exhaust port of the scroll compressor is equipped with a control valve, the reason why the pressure in the back pressure chamber 4 decreases from high is that the back pressure chamber 4 is not an absolutely sealed chamber. The gas in the back pressure chamber 4 will slowly leak outwards, and the leakage channels include the gap between the crankshaft 202 and the bracket 103. Because the leakage gap is small, the pressure in the back pressure chamber 4 will gradually decrease when there is no external gas injection. At this time, the flow area between the compression chamber 3 and the back pressure chamber 4 decreases, the damping of the gas passage increases, and the flow rate and pressure of the fluid entering the back pressure chamber 4 also decrease accordingly. This allows the pressure in the back pressure chamber 4 to decrease more quickly, making the vertical action on the moving plate 201 more balanced. Similarly, the reason why the pressure in the back pressure chamber 4 increases from low is that the area of ​​the pressure regulating passage increases, the damping of the gas passage decreases, and the flow rate and pressure of the gas entering the back pressure chamber 4 also increase. Since the change in the flow rate of the gas leaking outwards from the back pressure chamber 4 is small, the pressure in the back pressure chamber 4 increases. When the exhaust port of the scroll compressor is a throttling orifice, the main reason for the decrease in pressure in the back pressure chamber 4 is that the pressure regulating device 6 relieves the back pressure, while the pressure loss caused by gas leakage in other parts accounts for a small proportion; the reason for the increase in pressure in the back pressure chamber 4 is that the pressure relief of the back pressure chamber 4 by the pressure regulating device 6 is reduced. The rotation of the crankshaft 202 will eventually drive the moving disc 201 to revolve (rotate).

[0072] Preferred, such as Figure 6-13 As shown, the pressure regulating device 6 includes a slider, and the pressure regulating passage includes a pressure regulating section; the slider is at least partially disposed within the pressure regulating section, and the rotation of the crankshaft 202 enables the slider to move within the pressure regulating section; the sliding of the slider within the pressure regulating passage can change the pressure on both sides of the slider's movement direction, and the pressure difference on both sides of the slider's movement direction is negatively correlated with the rotational speed of the crankshaft 202.

[0073] The slider can move along with the rotation of the crankshaft 202. The movement of the slider adjusts the pressure on both sides of the slider's direction of movement, and makes the pressure difference on both sides of the slider negatively correlated with the rotational speed of the crankshaft 202. Here, negative correlation means that the higher the rotational speed of the crankshaft 202, the smaller the pressure difference, the smaller the damping effect of the pressure regulating section on the gas in the pressure regulating passage, and the greater the pressure of the gas after passing through the slider. Conversely, the lower the rotational speed of the crankshaft 202, the larger the pressure difference, the greater the damping effect of the pressure regulating section on the gas in the pressure regulating passage, and the lower the pressure of the gas after passing through the slider.

[0074] Since the back pressure chamber 4 is located on the pressure regulating passage, the sliding block adjusts the pressure difference on both sides of the pressure regulating device 6 (slider), thereby adjusting the pressure of the back pressure chamber 4.

[0075] The movement of the slider is related to the rotational speed of the crankshaft 202, which in turn makes the pressure of the back pressure chamber 4 related to the rotational speed of the crankshaft 202. This effectively makes the pressure of the back pressure chamber 4 change with the rotational speed of the crankshaft 202 (moving disk 201), thus improving the effectiveness and stability of the pressure regulation of the back pressure chamber 4.

[0076] Preferably, the pressure regulating device 6 further includes an elastic element, and the movement of the slider can cause the elastic element to deform.

[0077] Under the action of centrifugal force, the slider moves away from the axis of rotation of the crankshaft 202. It should be noted that the movement of the slider away from the axis of rotation of the crankshaft 202 does not mean that the pressure regulating device 6 is set on the crankshaft 202. It is sufficient that the pressure regulating device 6 is set on a structure connected to the crankshaft 202 and rotates with the crankshaft 202, such as on the eccentric sleeve 9. Under the action of centrifugal force, the slider still moves away from the axis of rotation of the crankshaft 202.

[0078] For ease of description, the direction in which the slider moves away from the axis of the crankshaft 202 is defined as the positive direction, and the direction opposite to the positive direction is defined as the negative direction. Under the action of centrifugal force, the slider moves in the positive direction, the elastic element is compressed and stores elastic potential energy, the rotational speed of the crankshaft 202 decreases, the centrifugal force on the slider decreases, the elastic element recovers and releases elastic potential energy, driving the slider to move in the negative direction; thus, the slider can follow the crankshaft 202 at different rotational speeds to move in different directions, thereby making the pressure in the back pressure chamber 4 change with the rotational speed of the crankshaft 202; improving the stability and speed of pressure adjustment in the back pressure chamber 4.

[0079] Preferred, such as Figure 6-13 As shown, the pressure regulating section includes a removable inner sleeve, and the slider is at least partially disposed within the inner sleeve.

[0080] A removable inner sleeve is installed within the pressure regulating section, and the slider is housed inside the inner sleeve. This reduces the installation difficulty of the pressure regulating device 6; simply place the pressure regulating device 6 inside the inner sleeve and then install the inner sleeve in the predetermined position. This configuration allows the pressure regulating device 6 and the inner sleeve to function as a single pressure regulating module, enabling rapid installation, replacement, and disassembly.

[0081] Example of a slider in the first form: Figure 6-8 As shown, the inner sleeve is a first housing 604, and the inner hole of the first housing 604 is a tapered hole 6042, with the small end of the tapered hole 6042 facing the air intake direction of the tapered hole 6042;

[0082] The slider is a first slider 601 and is capable of moving within the tapered hole 6042 along the axial direction of the tapered hole 6042.

[0083] When the slider is at the small end of the conical hole 6042, the flow area between the outer surface of the slider and the inner surface of the conical hole 6042 is small. When the slider moves to the large end, the flow area between the outer surface of the slider and the inner surface of the conical hole 6042 is large. As the slider moves from the small end to the large end of the conical hole 6042, the flow area between the outer surface of the slider and the inner surface of the conical hole 6042 gradually increases. Similarly, as the slider moves from the large end to the small end of the conical hole 6042, the flow area between the outer surface of the slider and the inner surface of the conical hole 6042 gradually decreases. When the gas flows through the flow channel between the slider and the conical hole 6042, the gas pressure decreases, thereby creating a pressure difference between the two sides of the slider (i.e., the pressure regulating device 6) in the direction of movement, thus effectively and reliably adjusting the pressure in the back pressure chamber 4.

[0084] Preferred, such as Figure 7 As shown, the first slider 601 includes an outer surface opposite to the inner surface of the tapered hole 6042, and the outer surface of the first slider 601 is a cylindrical surface; or, as... Figure 8 As shown, the outer surface of the first slider 601 is a conical surface, and the small end of the conical surface is in the same direction as the small end of the conical hole 6042.

[0085] When the outer surface of the first slider 601 is a cylindrical surface, after the gas flows through the minimum flow area formed between the first slider 601 and the inner surface of the conical hole 6042 (between the end of the cylindrical surface facing the small end of the conical hole 6042 and the inner surface of the conical hole 6042), there is a process of the flow area gradually increasing when the gas flows between the inner surface of the conical hole 6042 and the outer surface of the cylindrical surface. This can avoid noise and vibration generated after the gas passes through the minimum flow area.

[0086] When the outer surface of the first slider 601 is a conical surface, the cone angle of the conical surface is the same as the cone angle of the conical hole 6042; a flow channel with a constant flow area is formed between the inner surface of the conical hole 6042 and the outer surface of the first slider 601. Since the flow channel has a certain length and the flow area is constant, the flow channel has a better damping and pressure reduction effect on the gas.

[0087] Preferred, such as Figure 6-8 As shown, the elastic element is a spring, which includes a first spring 602 and a second spring 603. The first slider 601 includes a first end facing the small end of the tapered hole 6042 and a second end opposite to the first end of the first slider 601.

[0088] One end of the first spring 602 is connected to the first end of the first slider 601, and the other end of the first spring 602 is connected to the inner sleeve. One end of the second spring 603 is connected to the second end of the first slider 601, and the other end of the second spring 603 is connected to the inner sleeve.

[0089] A spring is provided at the first end and the second end of the first slider 601. When the first slider 601 moves, one of the two springs is stretched and the other is compressed. This increases the speed at which the first slider 601 changes its direction of motion during the transition from a slow to a steady state in the crankshaft 202, and improves the agility of the pressure regulating device 6 in adjusting the back pressure chamber 4.

[0090] The action of the two springs on the first slider 601 is as follows: when the crankshaft 202 changes from high speed to low speed, the first spring 602 gradually shortens from a stretched state and generates a pulling force on the first slider 601, while the second spring 603 gradually shortens from a compressed state and generates a pushing force on the first slider 601. The first spring 602 and the second spring 603 generate forces in the same direction on the first slider 601, which accelerates the sliding of the first slider 601 toward the small end of the tapered hole 6042. This accelerates the change in the minimum flow area between the outer surface of the first slider 601 and the inner surface of the tapered hole 6042, thereby adjusting the pressure of the back pressure chamber 4 more quickly.

[0091] Preferred, such as Figure 6-8 As shown, the pressure regulating device 6 also includes a support rod 610, one end of which faces the small end of the tapered hole 6042, and the other end of which faces the large end of the tapered hole 6042; the first slider 601 is movably disposed on the support rod 610.

[0092] As the gas compresses the first slider 601 when it flows through it, the friction between the gas and the first slider 601 causes the first slider 601 to vibrate during movement. By setting a support rod 610, the first slider 601 slides along the support rod 610, which prevents the first slider 601 from vibrating during movement, thus making the movement of the first slider 601 more stable and the pressure adjustment process of the back pressure chamber 4 more stable.

[0093] The axis of the support rod 610 can be made to coincide with the axis of the tapered hole 6042, so that in any plane perpendicular to the support rod 610, the flow path between the inner surface of the tapered hole 6042 and the outer surface of the first slider 601 is annular, thereby balancing the circumferential force on the first slider 601, reducing the friction between the first slider 601 and the support rod 610 during the movement, and making the movement of the first slider 601 more stable.

[0094] The small and large ends of the conical hole 6042 are provided with a fixing structure, which can be a stop bar. The stop bar has little effect on the gas entering and exiting the conical hole 6042. The axis of the stop bar is perpendicular to the axis of the conical hole 6042, and both ends of the stop bar are fixed on the inner surface of the conical hole 6042.

[0095] Example of a slider in the second form: Figure 8-13 As shown, the inner sleeve is a second housing 704, the inner hole of the second housing 704 is a sliding hole, the slider is a second slider 701, the outer surface of the second slider 701 is slidably attached to the inner wall surface of the sliding hole; the outer surface of the second slider 701 is provided with a first groove 702, the inlet end of the first groove 702 is close to the rotation axis of the crankshaft 202, and the outlet end of the first groove 702 is far away from the rotation axis of the crankshaft 202;

[0096] The second slider 701 is at least partially able to slide out of the sliding hole.

[0097] Pressure drop refers to the phenomenon where the fluid pressure decreases in the direction of flow due to factors such as resistance and friction when the fluid passes through a pipe or channel.

[0098] The first groove 702, which is covered by the inner wall of the inner sleeve, is responsible for reducing the pressure on the gas. The first groove 702, which is not covered by the inner wall of the inner sleeve, cannot reduce the pressure on the gas.

[0099] When the second slider 701 slides out of the sliding hole, the length of the first groove 702 covered by the inner wall of the inner sleeve is shortened. When the gas flows through the first groove 702, the pressure drop when the gas flows through the second slider 701 is reduced. The longer the second slider 701 slides out of the sliding hole, the shorter the length of the first groove 702 covered by the inner wall of the inner sleeve, and the smaller the pressure drop when the gas flows through the second slider 701. Similarly, the longer the second slider 701 enters the inner sleeve, the longer the length of the first groove 702 covered by the inner wall of the inner sleeve, and the greater the pressure drop when the gas flows through the first groove 702.

[0100] The faster the crankshaft 202 rotates, the longer the second slider 701 slides out of the sliding hole, and the smaller the pressure drop when the gas flows through the first groove 702; the slower the crankshaft 202 rotates, the shorter the length of the second slider 701 sliding out of the slider hole, and the greater the pressure drop when the gas flows through the first groove 702.

[0101] The outer surface of the second slider 701 is in contact with the inner surface of the sliding hole, so that the gas can only flow in the first groove 702, which improves the pressure drop effect of the first groove 702 on the gas; at the same time, the inner wall of the sliding hole has a guiding effect on the second slider 701, so that the second slider 701 will not vibrate in the radial direction of the sliding hole when it slides, thus improving the smoothness of the movement of the second slider 701.

[0102] Preferred, such as Figure 10 As shown, the outer surface of the second slider 701 is a cylindrical surface, and the first groove 702 is a spiral groove surrounding the outer surface of the second slider 701.

[0103] The outer surface of the second slider 701 is a cylindrical surface, and the first groove 702 is set as a spiral groove surrounding the cylindrical surface. When the axial length of the second slider 701 is constant, the length of the spiral groove can be set to be longer. The second slider 701 has a longer spiral groove with the same axial length, and the pressure drop that the second slider 701 can adjust is larger, which is beneficial to expanding the pressure adjustment range of the back pressure chamber 4.

[0104] When the high-pressure gas discharged from the scroll compressor contains lubricating oil, the spiral groove surrounds the second slider 701, allowing the lubricating oil to contact the inner surface of the inner sleeve in the spiral ring groove 1031 to lubricate the outer surface of the second slider 701. This improves the smoothness of the movement of the second slider 701, reduces the probability of crawling (stuttering) during the movement of the second slider 701, and improves the stability of the pressure regulation of the back pressure chamber 4.

[0105] Preferred, such as Figure 12-13 As shown, a baffle 606 is provided at one end of the inner sleeve away from the rotation axis of the crankshaft 202, and a vent hole 607 is provided on the baffle 606; the baffle 606 is fixed on the inner sleeve by a plurality of connecting members, and a gap is formed between two adjacent connecting members.

[0106] The baffle 606 prevents the second slider 701 from sliding completely out of the inner sleeve. The baffle 606 is fixed to the inner sleeve by a connector, so that the inner sleeve and the baffle 606 form a whole, which facilitates production and installation.

[0107] The connector can be configured as connecting rods 605. Multiple connecting rods 605 are evenly arranged along the circumferential direction of the inner sleeve. When the second slider 701 slides out of the inner sleeve, the multiple connecting rods 605 form a guiding structure for the second slider 701, preventing the second slider 701 from being subjected to radial force and causing bending moment, thus improving the smoothness of the movement of the second slider 701. The interval between two adjacent connecting rods 605 forms a channel between the outer surface of the second slider 701 and the inner wall of the pressure regulating passage; allowing the gas to leave the first groove 702 (entering the interval) after flowing out from the portion covered by the inner sleeve.

[0108] Preferred, such as Figure 12-13 As shown, the elastic element is a third spring 608, the inner sleeve is provided with an inner cavity, the inner cavity has an opening away from the rotation axis of the crankshaft 202, and the third spring 608 is disposed in the inner cavity and located between the second slider 701 and the baffle 606.

[0109] The third spring 608 is located in the inner cavity, which shortens the length of the pressure regulating device 6 and facilitates its installation; it also helps to miniaturize the scroll compressor.

[0110] Under the centrifugal force generated by the rotation of the crankshaft 202, the second slider 701 moves towards the baffle 606. The length of the first groove 702 covered by the inner sleeve becomes shorter (the first groove 702, which is not restricted by the inner wall of the inner sleeve, becomes longer), and the pressure drop of the gas passing through the pressure regulating device 6 becomes smaller. Since the second slider 701 also squeezes the third spring 608 when it moves, the third spring 608 stores elastic potential energy under compression. The rotational speed of the crankshaft 202 decreases, the centrifugal force on the second slider 701 decreases, and the second slider 701 moves towards the inner sleeve under the action of the third spring 608. The length of the first groove 702 covered by the inner sleeve becomes longer (the first groove 702, which is not restricted by the inner wall of the inner sleeve, becomes shorter), and the pressure drop of the gas passing through the pressure regulating device 6 becomes larger.

[0111] Example of a pressure regulating device installed on the venting channel (first venting channel):

[0112] like Figure 1-2 As shown, a first air inlet channel is provided between the compression chamber 3 and the back pressure chamber 4, and a first air outlet channel is provided between the back pressure chamber 4 and the low pressure chamber 5, connecting the back pressure chamber 4 and the low pressure chamber 5; the pressure regulating device 6 is disposed in the first air outlet channel.

[0113] The pressure regulating path includes a first air outlet channel and a second air outlet channel; the first air outlet channel is the pressure relief channel of the back pressure chamber 4; the pressure regulating device 6 is installed in the first air outlet channel to relieve and regulate the pressure of the back pressure chamber 4. That is, it meets the above-mentioned "case two".

[0114] Preferred, such as Figure 1-2 As shown, an eccentric sleeve 9 is provided between the first end of the crankshaft 202 and the moving disk 201. The eccentric sleeve 9 includes a first end face facing the moving disk 201 and a second end face opposite to the first end. An air gap 902 is formed between the first end face of the eccentric sleeve 9 and the moving disk 201. A first channel 711 is provided on the moving disk 201 to connect the compression chamber 3 and the air gap 902.

[0115] The eccentric sleeve 9 includes a journal 901 extending toward the moving disk 201. A first bearing 301 is sleeved on the journal 901. The inner ring of the first bearing 301 is connected to the journal 901, and the outer ring of the first bearing 301 is connected to the moving disk 201. A first gap 3011 is formed between the inner ring and the outer ring of the first bearing 301. The first gap 3011 connects the air gap 902 and the back pressure chamber 4.

[0116] The first intake channel includes a first channel 711, an air gap 902, and a first interval 3011. The air gap 902 and the first interval 3011 are existing structures. The existing structure is cleverly utilized, and the first channel 711 is set on the moving plate 201 to connect the compression chamber 3 and the back pressure chamber 4, which reduces the processing difficulty. Moreover, the high-pressure gas discharged from the scroll compressor contains lubricating oil. When the gas containing lubricating oil passes through the first interval 3011 on the first bearing 301, it lubricates the first bearing 301, improves the smoothness of the operation of the first bearing 301, and thus improves the smoothness of the rotation of the moving plate 201.

[0117] Preferred, such as Figure 1-2 As shown, a second groove is formed between the second end face of the eccentric sleeve 9 and the first end face of the crankshaft 202, and a second channel 712 and a third channel 713 are provided on the crankshaft 202;

[0118] The outlet of the third channel 713 faces the low-pressure chamber 5; one end of the second channel 712 is connected to the third channel 713, and the other end is connected to the second groove; the second groove is connected to the back pressure chamber 4; the pressure regulating device 6 is disposed in the third channel 713.

[0119] The first outlet passage sequentially includes a second groove, a second channel 712, and a third channel 713. When the back pressure chamber 4 needs pressure adjustment, the gas in the back pressure chamber 4 is released to the outside (pressure relief) through the pressure regulating device 6, increasing or decreasing the pressure. Since the gas contains lubricating oil, when the gas passes through the second groove, it lubricates the second end face of the eccentric sleeve 9 and the first end face of the crankshaft 202, thereby reducing the friction between the crankshaft 202 and the eccentric sleeve 9 and improving the compression efficiency of the scroll compressor. It should be noted that the eccentric sleeve 9 and the crankshaft 202 are not absolutely fixedly connected. The eccentric sleeve 9 can deflect at a certain small angle relative to the crankshaft 202 to avoid excessive compression and damage caused by impurities when the moving disc 201 rotates. That is, there will be a certain angle of relative rotation between the eccentric sleeve 9 and the crankshaft 202.

[0120] Preferred, such as Figure 1-2 As shown, the centerline of the second channel 712 coincides with the axis of the crankshaft 202; there are multiple third channels 713, which are evenly distributed along the circumference of the crankshaft 202, and the inlets of the multiple third channels 713 are connected to the outlet of the second channel 712.

[0121] The centerline of the second channel 712 coincides with the axis of the crankshaft 202, and the third channel 713 is evenly distributed along the circumference of the crankshaft 202, so that the crankshaft 202 can be more balanced in circumferential force when rotating; "multiple" includes "two", compared with "one" third channel 713, it can also avoid circumferential imbalance caused by the third channel 713 being set in the circumference of the crankshaft 202, and setting multiple third channels 713 can also accelerate the exhaust of gas.

[0122] When there are two third channels 713, the two third channels 713 can form a channel passing through the axis of the crankshaft 202. At this time, the first housing 604 inside the two third channels 713 can be combined into a first long housing 6041. The middle part of the first long housing 6041 is connected to the second channel 712. At this time, two tapered holes 6042 are provided inside the first long housing 6041.

[0123] Example of a pressure regulating device installed on the pressurization channel (second intake channel): (e.g.) Figure 3-5 As shown, a second air inlet channel is provided between the compression chamber 3 and the back pressure chamber 4, connecting the compression chamber 3 and the back pressure chamber 4; a second air outlet channel is provided between the back pressure chamber 4 and the low pressure chamber 5, connecting the back pressure chamber 4 and the low pressure chamber 5; the pressure regulating device 6 is disposed in the second air inlet channel.

[0124] The pressure regulating passage includes a second air intake passage and a second air outlet passage; the second air intake passage is a pressurization passage, and the pressure regulating device 6 is set in the second air intake passage to adjust the pressure of the back pressure chamber 4 by the amount of pressurization, which conforms to the above-mentioned "Case 1".

[0125] Preferred, such as Figure 3-5 As shown, an eccentric sleeve 9 is provided between the first end of the crankshaft 202 and the moving disk 201;

[0126] The second intake channel includes a first flow channel 801 connected end to end and disposed on the moving plate 201, a second flow channel 802 disposed on the eccentric sleeve 9, a third flow channel 803 disposed on the crankshaft 202, and a fourth flow channel 804 disposed on the crankshaft 202; the fourth flow channel 804 leads to the back pressure chamber 4, and the pressure regulating device 6 is disposed in the fourth flow channel 804.

[0127] By cleverly utilizing the existing structure, the second air intake channel includes a first flow channel 801, a second flow channel 802, a third flow channel 803, and a fourth flow channel 804. By setting up the first flow channel 801, second flow channel 802, third flow channel 803, and fourth flow channel 804 on the existing structure, the compression chamber 3 is connected to the back pressure chamber 4. This does not occupy additional existing space, nor does it increase the overall structural size. It also reduces manufacturing difficulty and facilitates modification of existing scroll compressors, thereby lowering production costs.

[0128] To better allow the gas in the compression chamber 3 to enter the first flow channel 801, the eccentric sleeve 9 and the moving plate 201 can be sealed together to prevent gas from leaking between the eccentric sleeve 9 and the moving plate 201.

[0129] Preferred, such as Figure 3-5 As shown, the eccentric sleeve 9 and the crankshaft 202 are connected by a crank pin 102, one end of which is inserted into the eccentric sleeve 9 and the other end is inserted into the crankshaft 202.

[0130] The crank pin 102 is provided with a fifth flow channel 805, one end of which is connected to the second flow channel 802 and the other end is connected to the third flow channel 803.

[0131] The second intake passage also includes a fifth flow channel 805; since the eccentric sleeve 9 will rotate at a certain small angle relative to the crankshaft 202, the fifth flow channel 805 on the crank pin 102 connects the second flow channel 802 and the third flow channel 803 to prevent gas leakage when passing between the eccentric sleeve 9 and the crankshaft 202.

[0132] A seal can be installed between the crank pin 102 and the eccentric sleeve 9 to prevent gas leakage when it enters the fifth flow channel 805 from the second flow channel 802.

[0133] Preferred, such as Figure 3-5 As shown, the centerline of the third flow channel 803 coincides with the axis of the crankshaft 202; there are multiple fourth flow channels 804, which are evenly distributed along the circumference of the crankshaft 202, and the inlets of the multiple fourth flow channels 804 are connected to the outlet of the third flow channel 803.

[0134] The centerline of the third flow channel 803 coincides with the axis of the crankshaft 202, and the fourth flow channel 804 is evenly distributed along the circumference of the crankshaft 202, so that the crankshaft 202 can be more balanced in circumferential force when rotating; "multiple" includes "two", compared with "one" fourth flow channel 804, it can also avoid circumferential imbalance caused by the fourth flow channel 804 being set in the circumference of the crankshaft 202, and setting multiple fourth flow channels 804 can also accelerate the gas discharge.

[0135] Preferred, such as Figure 3 As shown, the bracket 103 is provided with a shaft hole, and the crankshaft 202 is disposed through the shaft hole;

[0136] The inner wall of the shaft hole is provided with an annular groove 1031 surrounding the crankshaft 202, and a sealing part is provided between the annular groove 1031 and the low-pressure chamber 5; a second bearing 401 for supporting the crankshaft 202 is also provided between the shaft hole and the back pressure chamber 4. The second bearing 401 includes a first inner ring and a second outer ring, and a second gap 4011 is formed between the first inner ring and the second outer ring; the second gap 4011 connects the back pressure chamber 4 and the annular groove 1031, and the outlet of the fourth flow channel 804 faces the annular groove 1031.

[0137] The second intake passage also includes an annular groove 1031 and a second interval 4011; since the crankshaft 202 is in a rotating state, the annular groove 1031 can prevent the bracket 103 from blocking the outlet of the fourth flow channel 804; since the gas contains lubricating oil, when the gas entering the annular groove 1031 passes through the second interval 4011, the lubricating oil in the gas lubricates the second bearing 401, improving the smoothness of crankshaft 202.

[0138] The second air outlet channel consists of various gaps between the back pressure chamber 4 and the low pressure chamber 5. That is, the second air outlet channel is not specially set up. When the pressure of the back pressure chamber 4 needs to be reduced, the pressure regulating device 6 reduces the gas pressure entering the back pressure chamber 4. At the same time, the gas in the back pressure chamber 4 leaks to the low pressure chamber 5 through various gaps, thereby reducing the pressure of the back pressure chamber 4.

[0139] The present invention provides an air conditioner, including the aforementioned scroll compressor.

[0140] The present invention provides an automobile, including the air conditioner described above.

[0141] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features of the above-mentioned methods can be freely combined and superimposed.

[0142] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A scroll compressor, comprising a stationary disc (101), a moving disc (201), a crankshaft (202), and a bracket (103), wherein the stationary disc (101) is fixed on the bracket (103), the moving disc (201) is located between the stationary disc (101) and the bracket (103), and a compression chamber (3) is formed between the stationary disc (101) and the moving disc (201), characterized in that, A back pressure cavity (4) is formed between the moving disk (201) and the bracket (103), and a low pressure cavity (5) is provided on the side of the bracket (103) facing away from the back pressure cavity (4); the first end of the crankshaft (202) passes through the bracket (103) and is connected to the moving disk (201), and the second end of the crankshaft (202) is located on the side of the bracket (103) facing away from the back pressure cavity (4); The scroll compressor is provided with a pressure regulating passage, which is connected in sequence to the compression chamber (3), the back pressure chamber (4) and the low pressure chamber (5); a pressure regulating device (6) is provided on the pressure regulating passage, which can adjust the pressure of the back pressure chamber (4) according to the rotational speed of the crankshaft (202); The pressure regulating device (6) includes a slider, and the pressure regulating passage includes a pressure regulating section; The pressure regulating section includes a detachable inner sleeve, and the slider is at least partially disposed within the inner sleeve; the slider is at least partially disposed within the pressure regulating section, and the rotation of the crankshaft (202) enables the slider to move within the pressure regulating section; the sliding of the slider within the pressure regulating passage can change the pressure on both sides of the slider's movement direction, and the pressure difference on both sides of the slider's movement direction is negatively correlated with the rotational speed of the crankshaft (202); The inner sleeve is a second housing (704), the inner hole of the second housing (704) is a sliding hole, the slider is a second slider (701), the outer surface of the second slider (701) slides against the inner wall of the sliding hole; the outer surface of the second slider (701) is provided with a first groove (702), the inlet end of the first groove (702) is close to the rotation axis of the crankshaft (202), and the outlet end of the first groove (702) is far away from the rotation axis of the crankshaft (202); The second slider (701) is at least partially able to slide out of the sliding hole.

2. The scroll compressor according to claim 1, characterized in that, The pressure regulating device (6) also includes an elastic element, and the movement of the slider can cause the elastic element to deform.

3. The scroll compressor according to claim 2, characterized in that, The outer surface of the second slider (701) is a cylindrical surface, and the first groove (702) is a spiral groove surrounding the outer surface of the second slider (701).

4. The scroll compressor according to claim 3, characterized in that, A baffle (606) is provided at one end of the inner sleeve away from the rotation axis of the crankshaft (202), and a vent hole (607) is provided on the baffle (606); the baffle (606) is fixed on the inner sleeve by a plurality of connectors, and a gap is formed between two adjacent connectors.

5. The scroll compressor according to claim 4, characterized in that, The elastic element is a third spring (608), the inner sleeve is provided with an inner cavity, the inner cavity has an opening away from the rotation axis of the crankshaft (202), and the third spring (608) is disposed in the inner cavity and located between the second slider (701) and the baffle (606).

6. The scroll compressor according to claim 5, characterized in that, A first air inlet channel is provided between the compression chamber (3) and the back pressure chamber (4) to connect the compression chamber (3) and the back pressure chamber (4), and a first air outlet channel is provided between the back pressure chamber (4) and the low pressure chamber (5) to connect the back pressure chamber (4) and the low pressure chamber (5); the pressure regulating device (6) is provided in the first air outlet channel.

7. The scroll compressor according to claim 6, characterized in that, An eccentric sleeve (9) is provided between the first end of the crankshaft (202) and the moving disk (201). The eccentric sleeve (9) includes a first end face facing the moving disk (201) and a second end face opposite to the first end face. An air gap (902) is formed between the first end face of the eccentric sleeve (9) and the moving disk (201). A first channel (711) is provided on the moving disk (201) to connect the compression chamber (3) and the air gap (902). The eccentric sleeve (9) includes a journal (901) extending toward the moving disk (201), on which a first bearing (301) is sleeved. The inner ring of the first bearing (301) is connected to the journal (901), and the outer ring of the first bearing (301) is connected to the moving disk (201). A first gap (3011) is formed between the inner ring and the outer ring of the first bearing (301), and the first gap (3011) connects the air gap (902) and the back pressure chamber (4).

8. The scroll compressor according to claim 7, characterized in that, A second groove is formed between the second end face of the eccentric sleeve (9) and the first end face of the crankshaft (202), and a second channel (712) and a third channel (713) are provided on the crankshaft (202). The outlet of the third channel (713) faces the low-pressure chamber (5); one end of the second channel (712) is connected to the third channel (713), and the other end is connected to the second groove; the second groove is connected to the back pressure chamber (4); the pressure regulating device (6) is disposed in the third channel (713).

9. The scroll compressor according to claim 8, characterized in that, The centerline of the second channel (712) coincides with the axis of the crankshaft (202); there are multiple third channels (713), which are evenly distributed along the circumference of the crankshaft (202), and the inlets of the multiple third channels (713) are connected to the outlet of the second channel (712).

10. The scroll compressor according to claim 1, characterized in that, A second air inlet channel is provided between the compression chamber (3) and the back pressure chamber (4) to connect the compression chamber (3) and the back pressure chamber (4), and a second air outlet channel is provided between the back pressure chamber (4) and the low pressure chamber (5) to connect the back pressure chamber (4) and the low pressure chamber (5); the pressure regulating device (6) is provided in the second air inlet channel.

11. The scroll compressor according to claim 10, characterized in that, An eccentric sleeve (9) is provided between the first end of the crankshaft (202) and the moving disk (201). The second intake channel includes a first flow channel (801) connected end to end and disposed on the moving plate (201), a second flow channel (802) disposed on the eccentric sleeve (9), a third flow channel (803) disposed on the crankshaft (202), and a fourth flow channel (804) disposed on the crankshaft (202); the fourth flow channel (804) leads to the back pressure chamber (4), and the pressure regulating device (6) is disposed in the fourth flow channel (804).

12. The scroll compressor according to claim 11, characterized in that, The eccentric sleeve (9) and the crankshaft (202) are connected by a crank pin (102), one end of which is inserted into the eccentric sleeve (9) and the other end is inserted into the crankshaft (202). The crank pin (102) is provided with a fifth flow channel (805), one end of which is connected to the second flow channel (802) and the other end is connected to the third flow channel (803).

13. The scroll compressor according to claim 11, characterized in that, The centerline of the third flow channel (803) coincides with the axis of the crankshaft (202); there are multiple fourth flow channels (804), which are evenly distributed along the circumference of the crankshaft (202), and the inlets of the multiple fourth flow channels (804) are connected to the outlet of the third flow channel (803).

14. The scroll compressor according to claim 11, characterized in that, The bracket (103) is provided with a shaft hole, and the crankshaft (202) is disposed through the shaft hole; The inner wall of the shaft hole is provided with an annular groove (1031) surrounding the crankshaft (202), and a sealing part is provided between the annular groove (1031) and the low-pressure chamber (5); a second bearing (401) for supporting the crankshaft (202) is also provided between the shaft hole and the back pressure chamber (4), the second bearing (401) includes a first inner ring and a second outer ring, and a second gap (4011) is formed between the first inner ring and the second outer ring; the second gap (4011) connects the back pressure chamber (4) and the annular groove (1031), and the outlet of the fourth flow channel (804) faces the annular groove (1031).

15. An air conditioner, characterized in that, Includes the scroll compressor as described in any one of claims 1-14.

16. A car, characterized in that, Including the air conditioner as described in claim 15.

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