Scroll compressor and air conditioner capable of automatically adjusting back pressure

Abstract

The present invention provides a scroll compressor and air conditioner capable of automatically adjusting back pressure. The scroll compressor includes: a cover body connected to a stator plate, an exhaust chamber provided inside the cover body, one end of the exhaust port communicating with the compression chamber and the other end communicating with the exhaust chamber; an exhaust channel and a first channel provided on the cover body, a second channel provided on the bracket, one end of the exhaust channel communicating with the exhaust chamber and the other end capable of communicating with the outside of the cover body for exhaust, one end of the first channel communicating with the exhaust channel and the other end communicating with one end of the second channel, the other end of the second channel communicating with the back pressure chamber, a throttling pressure regulating device provided in the first channel and / or the second channel, the throttling pressure regulating device capable of automatically adjusting the throttling flow rate according to the magnitude of the incoming gas pressure. According to the present invention, the back pressure can be automatically adjusted according to the magnitude of the exhaust pressure, and back pressure regulation can be adapted to a wide range of working conditions.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a scroll compressor and an air conditioner capable of automatically adjusting back pressure. Background Art

[0002] As is well known, CO2 scroll compressors generate significant axial gas forces when compressing refrigerant, pushing the rotor and stator plates apart. This increases the clearance between the pumps, causing leakage and, in severe cases, preventing the normal and rapid establishment of a pressure differential. Existing technologies typically employ a backpressure chamber on the backside of the rotor plate to create a backpressure that balances the axial gas force. However, designing the backpressure chamber to balance the axial gas force remains a challenge in the industry.

[0003] Patent No. 202110437194.1 discloses a new movable scroll, back pressure structure and carbon dioxide compressor, such as Figure 1 As shown, the back pressure can be adjusted by the pressure relief holes and return holes on the moving disc, but the ability of this back pressure supply structure to adjust the back pressure is relatively limited, and it cannot adapt to the back pressure adjustment of a wide range of working conditions. In addition, there is gas leakage from the back pressure and the compression chamber, which causes repeated compression of the refrigerant. When the compressor is just started, because the exhaust pressure and back pressure have not yet been established, the moving disc and the static disc are pushed apart by the reaction force of the gas compression force, the gap becomes larger, and the leakage increases instantly, forming an invalid compression process, and the suction and exhaust pressure difference cannot be quickly established. The back pressure adjustment capability of the existing technical solution is limited and cannot adapt to the working requirements of automotive heat pump compressors (application ambient temperature -40°C to 80°C).

[0004] Patent No. 202022506710.5 discloses a back pressure pressure regulating structure, such as Figure 2 As shown in (a, b), this solution is to set a valve on the back of the moving disc to move back and forth with the moving disc to adjust the back pressure. However, the valve core of the regulating valve in this technical solution conflicts with the back of the moving disc, which is bound to generate an overturning force on the moving disc, affecting the operating stability of the moving disc. At the same time, the valve core will also generate friction power consumption with the back of the moving disc, affecting the performance of the compressor.

[0005] Patent No. 201811545156.2 discloses a one-way regulating valve back pressure regulating structure, such as Figure 3 、 Figure 4As shown, this one-way valve structure is only suitable for a limited range of operating conditions. Back pressure is only provided by the intermediate compression chamber. For a scroll compressor with a fixed volume ratio, when the suction pressure remains unchanged, the back pressure oil supply hole opened at a fixed position on the moving disk can only provide a fixed back pressure and cannot obtain a higher back pressure. Therefore, this solution cannot adapt to a wider range of operating conditions. For carbon dioxide scroll compressors, due to the large axial gas force, that is, the axial force pushing the moving and static disks apart is large, the back pressure that needs to be overcome is also large. The structure that relies on the fixed pressure supply of the intermediate compression chamber cannot meet the actual use requirements.

[0006] Since the back pressure supply structure of the scroll compressor in the prior art has technical problems such as limited ability to adjust the back pressure and inability to adapt to back pressure regulation in a wide range of working conditions, the present invention studies and designs a scroll compressor and air conditioner that can automatically adjust the back pressure. Summary of the Invention

[0007] Therefore, the technical problem to be solved by the present invention is to overcome the defects of the back pressure supply structure of the scroll compressor in the prior art, which has a relatively limited ability to adjust the back pressure and cannot adapt to the back pressure adjustment in a wide range of working conditions, thereby providing a scroll compressor and air conditioner that can automatically adjust the back pressure.

[0008] In order to solve the above problems, the present invention provides a scroll compressor capable of automatically adjusting back pressure, comprising:

[0009] A movable plate, a stationary plate, a bracket and a cover body, wherein a back pressure chamber is provided inside the bracket to provide back pressure to the movable plate, the movable plate and the stationary plate engage to form a compression chamber, an exhaust port is provided on the stationary plate, the cover body is connected to the stationary plate, an exhaust chamber is provided inside the cover body, one end of the exhaust port is communicated with the compression chamber, and the other end is communicated with the exhaust chamber;

[0010] The cover body is further provided with an exhaust channel and a first channel, and the bracket is provided with a second channel, one end of the exhaust channel is connected to the exhaust chamber, and the other end can be connected to the outside of the cover body for exhaust, one end of the first channel is connected to the exhaust channel, and the other end is connected to one end of the second channel, and the other end of the second channel is connected to the back pressure chamber, and a throttling pressure regulating device is provided in the first channel and / or the second channel, and the throttling pressure regulating device can automatically adjust the size of the throttling flow according to the size of the incoming gas pressure;

[0011] When the gas pressure is relatively high, the throttling opening of the throttling pressure regulating device is relatively large, allowing a relatively large flow of gas to pass through. When the gas pressure is relatively low, the throttling opening of the throttling pressure regulating device is relatively small, allowing a relatively small flow of gas to pass through.

[0012] In some embodiments, the throttling pressure regulating device includes a first valve core, the first channel and / or the second channel include a third channel and a fourth channel connected to each other, the inner diameter of the third channel is smaller than the inner diameter of the fourth channel, and the third channel is located upstream of the fourth channel along the direction of air flow, the first valve core is located in the third channel and the fourth channel and can move in the third channel and the fourth channel, a channel for throttling is formed between the outer peripheral wall of the first valve core and the inner peripheral wall of the third channel, one axial end of the first valve core is opposite to the direction of air flow so as to withstand the pressure of the air flow, when the gas pressure is relatively large, the length of the shaft section of the first valve core entering the fourth channel is relatively long, and the length of the shaft section located in the third channel is relatively short; when the gas pressure is relatively small, the length of the shaft section of the first valve core entering the fourth channel is relatively short, and the length of the shaft section located in the third channel is relatively long.

[0013] In some embodiments, an outer spiral groove is provided on the outer peripheral wall of the first valve core, and / or an inner spiral groove is provided on the inner peripheral wall of the third channel to form the throttling channel. When the gas pressure is relatively large, the length of the axial section of the first valve core located in the third channel is relatively short, the length of throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the axial section of the first valve core located in the third channel is relatively long, the length of throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

[0014] In some embodiments, there is a first gap between the outer circumferential wall of the first valve core and the inner circumferential wall of the third channel to form the throttling channel. When the gas pressure is relatively large, the length of the axial section of the first valve core located in the third channel is relatively short, the length of the throttling through the first gap is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the axial section of the first valve core located in the third channel is relatively long, the length of the throttling through the first gap is relatively long, and the throttling opening is relatively small.

[0015] In some embodiments, when the axial end of the first valve core is not subjected to gas pressure, the first valve core is entirely or mostly located in the third channel; when the gas pressure borne by the axial end of the first valve core increases, the length of the first valve core entering the fourth channel increases, resulting in a decrease in the throttling effect; when the gas pressure borne by the axial end of the first valve core decreases, the length of the first valve core entering the fourth channel decreases, resulting in an increase in the throttling effect.

[0016] In some embodiments, a first elastic member is further included, one end of which is fixed and the other end is connected to the first valve core, capable of providing an elastic restoring force for the first valve core to move in the direction of the third channel, and the other end of the first elastic member is connected to the end of the first valve core opposite to the axial end.

[0017] In some embodiments, a first accommodating groove is defined inside the first valve core, a portion of the first elastic member is passed through the first accommodating groove, and the other end of the first elastic member is fixedly connected to or abuts against the bottom of the first accommodating groove.

[0018] In some embodiments, a first annular boss extending radially outward is formed at the other axial end of the first valve core, and a first step is formed at the junction of the third channel and the fourth channel. The first annular boss can be matched and engaged with the first step to form a limit; a first limit member is provided at the end of the fourth channel away from the third channel, the first limit member is fixed to the cover body or the bracket, one end of the first elastic member is fixed to the first limit member, and the first limit member is also provided with a through hole for accommodating the passage of gas.

[0019] In some embodiments, the throttling pressure regulating device includes a first valve housing and a second valve core. The first valve housing is located in the first channel and / or the second channel. The interior of the first valve housing has a first internal channel. The second valve core is arranged in the first internal channel and can move in the first internal channel. The first internal channel includes a fifth channel and a sixth channel connected to each other. The inner diameter of the fifth channel is smaller than that of the sixth channel, and the fifth channel is located upstream of the sixth channel along the flow pattern of the airflow. A channel for throttling is formed between the outer circumferential wall of the second valve core and the inner circumferential wall of the first valve housing. One axial end of the second valve core is opposite to the direction of airflow so that it can withstand the pressure of the airflow. When the gas pressure is relatively large, the length of the shaft section of the second valve core entering the sixth channel is relatively long, and the length of the shaft section located in the fifth channel is relatively short; when the gas pressure is relatively small, the length of the shaft section of the second valve core entering the sixth channel is relatively short, and the length of the shaft section located in the fifth channel is relatively long.

[0020] In some embodiments, an outer spiral groove is provided on the outer circumferential wall of the second valve core, and / or an inner spiral groove is provided on the inner circumferential wall of the fifth channel to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the second valve core entering the sixth channel is relatively long, and the length of the shaft section located in the fifth channel is relatively short. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the shaft section of the second valve core entering the sixth channel is relatively short, and the length of the shaft section located in the fifth channel is relatively long. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

[0021] In some embodiments, a second gap is provided between the outer peripheral wall of the second valve core and the inner peripheral wall of the fifth channel to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the second valve core entering the sixth channel is relatively long, and the length of the shaft section located in the fifth channel is relatively short. The length throttling through the second gap is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively small, the length of the shaft section of the second valve core entering the sixth channel is relatively short, and the length of the shaft section located in the fifth channel is relatively long. The length throttling through the second gap is relatively long, and the throttling opening is relatively small.

[0022] In some embodiments, when the axial end of the second valve core is not subjected to gas pressure, the second valve core is entirely or mostly located in the fifth channel; when the axial end of the second valve core is subjected to increased gas pressure, the length of the second valve core entering the sixth channel increases, resulting in a decrease in the throttling effect; when the axial end of the second valve core is subjected to decreased gas pressure, the length of the second valve core entering the sixth channel decreases, resulting in an increase in the throttling effect.

[0023] In some embodiments, a second elastic member is further included, one end of which is fixed to the first valve housing and the other end is connected to the second valve core, capable of providing an elastic restoring force for the second valve core to move in the direction of the fifth channel, and the other end of the second elastic member is connected to the end of the second valve core opposite to the axial end.

[0024] In some embodiments, a second accommodating groove is defined inside the second valve core, a portion of the second elastic member is passed through the second accommodating groove, and the other end of the second elastic member is fixedly connected to or abuts against the bottom of the second accommodating groove.

[0025] In some embodiments, a second annular boss extending radially outward is formed at the other axial end of the second valve core, and a second step is formed at the junction of the fifth channel and the sixth channel. The second annular boss can be matched and engaged with the second step to form a limit; a second limiter is provided at the end of the first valve housing located downstream in the direction of air flow, the second limiter is fixed to the first valve housing, one end of the second elastic member is fixed to the second limiter, and the second limiter is also provided with a through hole for accommodating gas passage.

[0026] In some embodiments, a first pressure relief channel is further provided inside the bracket, and a pressure relief regulating valve is provided in the first pressure relief channel. One end of the first pressure relief channel is connected to the back pressure chamber, and the other end is connected to the suction side of the scroll compressor. The pressure relief regulating valve can throttle the inside of the first pressure relief channel to adjust the flow rate in the first pressure relief channel.

[0027] In some embodiments, the pressure relief regulating valve can automatically adjust the size of the throttling flow according to the size of the incoming gas pressure in the first pressure relief channel. When the gas pressure is relatively large, its throttling opening is relatively large, and a relatively large flow of gas can be allowed to pass through. When the gas pressure is relatively small, its throttling opening is relatively small, and a relatively small flow of gas can be allowed to pass through, so as to relieve the pressure in the back pressure chamber to the suction side of the scroll compressor.

[0028] In some embodiments, the pressure relief regulating valve includes a second valve housing and a third valve core, the second valve housing is located in the first pressure relief channel, the interior of the second valve housing has a second internal channel, the second valve core is arranged in the second internal channel and can move in the second internal channel, the second internal channel includes a seventh channel and an eighth channel connected to each other, the inner diameter of the seventh channel is smaller than the eighth channel, and the seventh channel is located upstream of the eighth channel along the direction of air flow, a channel for throttling is formed between the outer circumferential wall of the third valve core and the inner circumferential wall of the second valve housing, one axial end of the third valve core is opposite to the direction of air flow so as to withstand the pressure of the air flow, when the gas pressure is relatively large, the length of the shaft section of the third valve core entering the eighth channel is relatively long, and the length of the shaft section located in the seventh channel is relatively short, when the gas pressure is relatively small, the length of the shaft section of the third valve core entering the eighth channel is relatively short, and the length of the shaft section located in the seventh channel is relatively long.

[0029] In some embodiments, an outer spiral groove is provided on the outer peripheral wall of the third valve core, and / or an inner spiral groove is provided on the inner peripheral wall of the seventh channel to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the third valve core entering the eighth channel is relatively long, and the length of the shaft section located in the seventh channel is relatively short. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively small, the length of the shaft section of the third valve core entering the eighth channel is relatively short, and the length of the shaft section located in the seventh channel is relatively long. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

[0030] In some embodiments, a third gap is provided between the outer peripheral wall of the third valve core and the inner peripheral wall of the seventh channel to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the third valve core entering the eighth channel is relatively long, and the length of the shaft section located in the seventh channel is relatively short. The length throttling through the third gap is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively small, the length of the shaft section of the third valve core entering the eighth channel is relatively short, and the length of the shaft section located in the seventh channel is relatively long. The length throttling through the third gap is relatively long, and the throttling opening is relatively small.

[0031] In some embodiments, a third elastic member is further included, one end of which is fixed to the second valve housing and the other end is connected to the third valve core, capable of providing an elastic restoring force for the third valve core to move in the direction of the seventh channel, and the other end of the third elastic member is connected to the end of the third valve core opposite to the axial end.

[0032] In some embodiments, a third accommodating groove is opened inside the third valve core, a partial section of the third elastic member is passed through the third accommodating groove, and the other end of the third elastic member is fixedly connected or abutted against the bottom of the third accommodating groove.

[0033] In some embodiments, the pressure relief regulating valve is a columnar throttling spiral pin with a spiral throttling groove provided on its outer peripheral wall. The throttling spiral pin is provided in the first pressure relief channel and can achieve a fixed throttling effect on the fluid.

[0034] In some embodiments, a first one-way valve and a fourth elastic member are further provided in the first pressure relief channel, one end of the fourth elastic member is connected to the pressure relief regulating valve, and the other end is connected to the first one-way valve, and the first one-way valve only allows gas to flow out from the back pressure chamber toward the suction side of the scroll compressor.

[0035] In some embodiments, a second pressure relief channel is provided on the movable disc, one end of the second pressure relief channel is connected to the low-pressure chamber in the compression chamber, and the other end is connected to the back-pressure chamber, so that the pressure in the back-pressure chamber can be relieved into the low-pressure chamber. The compression chamber includes a low-pressure chamber, a medium-pressure chamber and a high-pressure chamber, which are respectively a high-pressure chamber, a medium-pressure chamber and a low-pressure chamber in order of pressure from large to small. The pressure of the high-pressure chamber is equal to the pressure of the exhaust chamber.

[0036] In some embodiments, an initial back pressure supply channel is provided on the moving disk, one end of the initial back pressure supply channel is connected to the low pressure chamber or the medium pressure chamber in the compression chamber, and the other end is connected to the back pressure chamber, so that the pressure in the low pressure chamber or the medium pressure chamber can be released into the back pressure chamber. The compression chamber includes a low pressure chamber, a medium pressure chamber and a high pressure chamber, which are respectively a high pressure chamber, a medium pressure chamber and a low pressure chamber in order of pressure from large to small, and the pressure of the high pressure chamber is equal to the pressure of the exhaust chamber.

[0037] In some embodiments, a second one-way valve is further provided in the initial back pressure supply channel, and the second one-way valve only allows fluid to flow from the low pressure chamber or the medium pressure chamber to the back pressure chamber; and / or, a second throttle valve is further provided in the initial back pressure supply channel, and the second throttle valve is a columnar throttling spiral pin, and a spiral throttling groove is provided on its outer peripheral wall, and the second throttle valve can achieve a fixed throttling effect on the fluid.

[0038] In some embodiments, when a second one-way valve and a second throttle valve are included at the same time, the second one-way valve is also a one-way ball valve, and a fifth elastic member is also provided in the initial back pressure supply channel, one end of the fifth elastic member is connected to the second throttle valve, and the other end is connected to the second one-way valve.

[0039] In some embodiments, the second channel includes a second channel 1 and a second channel 2, the second channel 1 extends along the axial direction of the bracket, the central axis of the second channel 2 forms an angle between 0 and 90 degrees with the axis of the bracket, one end of the second channel 1 is located at the axial end of the bracket opposite to the cover body, and is connected to the first channel, the other end of the second channel 1 is connected to one end of the second channel 2, and the other end of the second channel 2 extends to connect with the back pressure chamber.

[0040] In some embodiments, when the throttling pressure regulating device includes a first valve housing and a second valve core, and the first valve housing is located in the second channel, a notch is provided on the first valve housing at a position where it connects with the second channel.

[0041] The present invention also provides an air conditioner, comprising the scroll compressor capable of automatically adjusting back pressure as described in any of the preceding items.

[0042] The scroll compressor and air conditioner capable of automatically adjusting back pressure provided by the present invention have the following beneficial effects:

[0043] 1. The present invention can effectively guide the exhaust gas in the exhaust channel into the back pressure chamber to provide back pressure in the back pressure chamber by providing a first channel on the cover body and a second channel on the bracket, and a throttling pressure regulating device is provided in the first and / or second channel, which can adjust the flow rate according to the pressure of the incoming air flow. When the incoming flow pressure is large, the flow rate is automatically controlled to be large, which can provide a large pressure to the back pressure chamber when the exhaust pressure is high, thereby effectively balancing the force on the moving disk, preventing the moving disk from being pushed by the exhaust pressure to the point of gas leakage between the moving disk and the static disk, and when the incoming flow pressure is small, the flow rate is automatically controlled to be small. , which can provide a smaller pressure to the back pressure chamber when the exhaust pressure is small, thereby effectively balancing the force on the moving disc, preventing the moving disc from being pushed by the exhaust pressure to the position where gas leakage occurs between the moving disc and the static disc. At the same time, it can also prevent the moving disc from overturning or being severely worn due to excessive back pressure. Therefore, the back pressure supply structure of the present invention can automatically adjust the back pressure according to the size of the exhaust pressure, and can adapt to back pressure regulation in a wide range of working conditions; solve the problem of expanding the back pressure regulation capability of the compressor, so that the compressor can adapt to a wider range of application conditions; solve the problem of slow back pressure response, reduce the time it takes to establish the suction and exhaust pressure difference, so that the back pressure can be quickly adjusted to the required size;

[0044] 2. The present invention also uses the initial back pressure supply channel to guide the medium pressure or low pressure in the compression chamber to the back pressure chamber through the initial back pressure supply channel when there is not enough exhaust gas at the initial stage of the compressor startup, thereby providing back pressure to the moving plate, effectively solving the problem that when the compressor is just started, the exhaust pressure and back pressure have not yet been established, the moving plate and the static plate are pushed apart by the reaction force of the gas compression force, the gap becomes larger, the leakage increases instantly, an invalid compression process is formed, and the suction and exhaust pressure difference cannot be established quickly; that is, it solves the problem of invalid compression when the compressor is started, and reduces the time for establishing the suction and exhaust pressure difference; and by arranging a one-way valve structure in the initial back pressure supply channel, it can reduce the repeated compression process caused by the back pressure chamber blowing into the compression chamber.

[0045] 3. Therefore, the present invention adopts a multi-channel pressure supply and pressure regulation scheme to realize the provision of back pressure through different channels in the initial stage of compression startup and the later stage of startup, so that the compressor can quickly establish a pressure difference, and by setting a corresponding pressure regulating device, a wider range of pressure regulation capabilities is achieved, so that the compressor can broaden its application range, adapt to a wider range of working conditions, and simultaneously meet the application requirements of ultra-low temperature heating and high temperature refrigeration of vehicle-mounted air conditioners. The multi-channel back pressure supply (preferably carbon dioxide) scroll compressor of the present invention provides appropriate back pressure by connecting different back pressure induction channels at different times when the compressor starts running, so as to achieve rapid establishment of back pressure and rapid establishment of suction and exhaust pressure difference, and at the same time can more accurately adjust the back pressure.

[0046] 4. The present invention sets a pressure relief regulating valve in the first pressure relief channel on the bracket. The pressure relief regulating valve can achieve stable pressure relief or adjust the flow rate according to the pressure of the incoming air flow. When the incoming flow pressure is large, the flow rate passing through is automatically controlled to be large, which can make the back pressure chamber pressure high and release a large pressure to it, thereby preventing the back pressure chamber from being too high and causing the movable disc to overturn or wear, and preventing the movable disc from being pushed by the exhaust pressure. When the incoming flow pressure is small, the flow rate passing through is automatically controlled to be small, which can make the back pressure chamber pressure small and release a small pressure to the back pressure chamber, thereby preventing the back pressure chamber from being too small and causing gas leakage between the movable disc and the static disc. Therefore, the pressure relief regulating structure of the present invention can automatically adjust the degree of pressure relief according to the size of the back pressure chamber pressure, which can prevent the movable disc from overturning or wearing while also preventing gas leakage between the movable disc and the static disc. BRIEF DESCRIPTION OF THE DRAWINGS

[0047] Figure 1 1 is an internal cross-sectional view of a scroll compressor embodiment 1 of the present invention (state 1); Figure 1-1 yes Figure 1 A partial enlarged view of part A1 in state 1;

[0048] Figure 1-2 yes Figure 1 A partial enlarged view of part A1 in state 2;

[0049] Figure 1-3 yes Figure 1 A partial enlarged view of part B1;

[0050] Figure 1-4 yes Figure 1 A partial enlarged view of the C1 part;

[0051] Figure 1-5 for Figure 1-1 An enlarged structural diagram of the first valve core in the throttling device;

[0052] Figure 1-6 for Figure 1-1An enlarged structural diagram of the first position-limiting member in the throttling device;

[0053] Figure 2 is an internal cross-sectional view of a scroll compressor according to a second embodiment of the present invention;

[0054] Figure 2-1 yes Figure 2 A partial enlarged view of part A2;

[0055] Figure 2-2 yes Figure 2 A partial enlarged view of part B2;

[0056] Figure 2-3 yes Figure 2 A partial enlarged view of the C2 part;

[0057] Figure 3 is an internal cross-sectional view of a scroll compressor according to a third embodiment of the present invention;

[0058] Figure 3-1 yes Figure 3 A partial enlarged view of part A3;

[0059] Figure 3-2 yes Figure 3 A partial enlarged view of part B3;

[0060] Figure 3-3 yes Figure 3 A partial enlarged view of the C3 part;

[0061] Figure 4 is an internal cross-sectional view of a scroll compressor according to a fourth embodiment of the present invention;

[0062] Figure 4-1 yes Figure 4 A partial enlarged view of the A4 portion;

[0063] Figure 4-2 yes Figure 4 A partial enlarged view of part B4;

[0064] Figure 4-3 yes Figure 4 A partial enlarged view of the C4 part;

[0065] Figure 5 is an internal cross-sectional view of a scroll compressor according to a fifth embodiment of the present invention;

[0066] Figure 5-1 yes Figure 5 A partial enlarged view of the A5 part;

[0067] Figure 5-2 yes Figure 5 A partial enlarged view of part B5;

[0068] Figure 5-3 yes Figure 5 A partial enlarged view of the C5 part;

[0069] Figure 6 is an internal cross-sectional view of a scroll compressor according to a sixth embodiment of the present invention;

[0070] Figure 6-1 yes Figure 6 A partial enlarged view of the A6 section;

[0071] Figure 6-2 yes Figure 6 A partial enlarged view of part B6;

[0072] Figure 6-3 yes Figure 6 A partial enlarged view of the C6 part;

[0073] Figure 7 is an internal cross-sectional view of a scroll compressor according to a seventh embodiment of the present invention;

[0074] Figure 7-1 yes Figure 7 A partial enlarged view of part A7;

[0075] Figure 7-2 yes Figure 7 A partial enlarged view of the B7 part;

[0076] Figure 7-3 yes Figure 7 A partial enlarged view of the C7 part;

[0077] Figure 8 is an internal cross-sectional view of Example 8 of the scroll compressor of the present invention;

[0078] Figure 8-1 yes Figure 8 A partial enlarged view of the A8 part;

[0079] Figure 8-2 yes Figure 8 A partial enlarged view of part B8;

[0080] Figure 8-3 yes Figure 8 A partial enlarged view of the C8 part;

[0081] Figure 9 is an internal cross-sectional view of a scroll compressor according to a ninth embodiment of the present invention;

[0082] Figure 9-1 yes Figure 9 A partial enlarged view of part A9;

[0083] Figure 9-2 yes Figure 9 A partial enlarged view of the B9 part;

[0084] Figure 9-3 yes Figure 9 A partial enlarged view of the C9 part;

[0085] Figure 10 is an internal cross-sectional view of a scroll compressor according to embodiment 10 of the present invention;

[0086] Figure 10-1 yes Figure 10 A partial enlarged view of part A10;

[0087] Figure 10-2 yes Figure 10 A partial enlarged view of part B10;

[0088] Figure 10-3 yes Figure 10 A partial enlarged view of the C10 part;

[0089] Figure 11 is an internal cross-sectional view of Example 11 of the scroll compressor of the present invention;

[0090] Figure 11-1 yes Figure 11 A partial enlarged view of the A11 part;

[0091] Figure 11-2 yes Figure 11 A partial enlarged view of the B11 part;

[0092] Figure 11-3 yes Figure 11 A partial enlarged view of the C11 part;

[0093] Figure 12 is an internal cross-sectional view of a scroll compressor according to embodiment 12 of the present invention;

[0094] Figure 12-1 yes Figure 12 A partial enlarged view of part A12;

[0095] Figure 12-2 yes Figure 12 A partial enlarged view of the B12 part;

[0096] Figure 12-3 yes Figure 12 A partial enlarged view of the C12 part;

[0097] Figure 13 is an internal cross-sectional view of Example 13 of the scroll compressor of the present invention;

[0098] Figure 13-1 yes Figure 13 A partial enlarged view of part A13;

[0099] Figure 13-2 yes Figure 13 A partial enlarged view of part B13;

[0100] Figure 13-3 yes Figure 13 A partial enlarged view of the C13 section;

[0101] Figure 14 is an internal cross-sectional view of a scroll compressor according to a fourteenth embodiment of the present invention;

[0102] Figure 14-1 yes Figure 14 A partial enlarged view of part A14;

[0103] Figure 14-2 yes Figure 14 A partial enlarged view of part B14;

[0104] Figure 14-3 yes Figure 14 A partial enlarged view of part C14.

[0105] The reference numerals indicate:

[0106] 1. Moving plate; 2. Static plate; 3. Bracket; 31. First pressure relief channel; 4. Cover; 41. Exhaust channel; 5. Back pressure chamber; 6. Exhaust port; 7. Exhaust chamber; 81. First channel; 82. Second channel; 821. Second channel 1; 822. Second channel 2; 83. Third channel; 84. Fourth channel; 85. Fifth channel; 86. Sixth channel; 87. First step; 88. First stopper; 89. Second step; 810. Second stopper; 9. Throttling pressure regulating device; 91. First valve core; 911. First annular boss; 912. First external thread; 92. First elastic member; 93. First A receiving groove; 94, a first valve housing; 941, a notch; 95, a second valve core; 951, a second annular boss; 96, a second elastic member; 97, a second receiving groove; 10, a pressure relief regulating valve; 101, a second valve housing; 102, a third valve core; 103, a seventh channel; 104, an eighth channel; 105, a third elastic member; 106, a third receiving groove; 107, a first one-way valve; 108, a fourth elastic member; 11, a compression chamber; 12, an initial back pressure supply channel; 13, a second one-way valve; 14, a second throttle valve; 15, a fifth elastic member; 16, a second pressure relief channel; 17, a housing; 18, a filter element. DETAILED DESCRIPTION

[0107] like Figure 1-14 As shown, the present invention provides a scroll compressor capable of automatically adjusting back pressure, comprising:

[0108] A movable plate 1, a static plate 2, a bracket 3, and a cover 4. The bracket 3 is provided with a back pressure chamber 5 to provide back pressure to the movable plate 1. The movable plate 1 and the static plate 2 are engaged to form a compression chamber 11. The static plate 2 is provided with an exhaust port 6. The cover 4 is connected to the static plate 2. The cover 4 is provided with an exhaust chamber 7. One end of the exhaust port 6 is connected to the compression chamber 11, and the other end is connected to the exhaust chamber 7.

[0109] The cover body 4 is further provided with an exhaust channel 41 and a first channel 81, and the bracket 3 is provided with a second channel 82. One end of the exhaust channel 41 is connected to the exhaust chamber 7, and the other end can be connected to the outside of the cover body 4 for exhaust. One end of the first channel 81 is connected to the exhaust channel 41, and the other end is connected to one end of the second channel 82. The other end of the second channel 82 is connected to the back pressure chamber 5. A throttling pressure regulating device 9 is provided in the first channel 81 and / or the second channel 82. The throttling pressure regulating device 9 can automatically adjust the size of the throttling flow according to the size of the incoming gas pressure;

[0110] When the gas pressure is relatively high, the throttling opening of the throttling pressure regulating device 9 is relatively large, allowing a relatively large flow of gas to pass through. When the gas pressure is relatively low, the throttling opening of the throttling pressure regulating device 9 is relatively small, allowing a relatively small flow of gas to pass through.

[0111] The present invention can effectively guide the exhaust gas in the exhaust channel into the back pressure chamber to provide back pressure in the back pressure chamber by providing a first channel on the cover body and a second channel on the bracket, and provides a throttling pressure regulating device in the first and / or second channel, which can adjust the flow rate according to the pressure of the incoming air flow. When the incoming flow pressure is relatively large, the flow rate is automatically controlled to be relatively large, which can provide a relatively large pressure to the back pressure chamber when the exhaust pressure is high, thereby effectively balancing the force on the moving disk, preventing the moving disk from being pushed by the exhaust pressure to the point of gas leakage between the moving disk and the static disk, and automatically controlling the flow rate to be relatively small when the incoming flow pressure is relatively small. It can provide a smaller pressure to the back pressure chamber when the exhaust pressure is small, thereby effectively balancing the force on the moving disk, preventing the moving disk from being pushed by the exhaust pressure to the point of gas leakage between the moving disk and the static disk, and at the same time preventing the moving disk from overturning or severe wear due to excessive back pressure. Therefore, the back pressure supply structure of the present invention can automatically adjust the back pressure according to the size of the exhaust pressure, and can adapt to back pressure regulation in a wide range of working conditions; solve the problem of expanding the back pressure regulation capability of the compressor, so that the compressor can adapt to a wider range of application conditions; solve the problem of slow back pressure response, reduce the time to establish the suction and exhaust pressure difference, so that the back pressure can be quickly adjusted to the required size.

[0112] The present invention solves the following technical problems

[0113] 1. Solve and expand the ability of compressor back pressure regulation to enable the compressor to adapt to a wider range of application conditions;

[0114] 2. Solve the problem of invalid compression when the compressor starts, and reduce the time it takes to establish the suction and exhaust pressure difference;

[0115] 3. Solve the problem of slow back pressure response and reduce the time it takes to establish the suction and exhaust pressure difference;

[0116] 4. Reduce the repeated compression process caused by gas leakage from the back pressure chamber to the compression chamber.

[0117] Beneficial effects:

[0118] The present invention adopts a multi-channel pressure supply and pressure regulation scheme to provide back pressure through different channels in the initial stage of compression startup and the later stage of startup, so that the compressor can quickly establish a pressure difference, and by setting a corresponding pressure regulating device, a wider range of pressure regulation capabilities is achieved, so that the compressor can broaden its application range, adapt to a wider range of working conditions, and simultaneously meet the application requirements of ultra-low temperature heating and high temperature refrigeration of vehicle-mounted air conditioners. The multi-channel back pressure supply (preferably carbon dioxide) scroll compressor of the present invention provides appropriate back pressure by connecting different back pressure induction channels at different times when the compressor starts running, so as to quickly establish back pressure and quickly establish the suction and exhaust pressure difference, and at the same time more accurately adjust the back pressure.

[0119] In some embodiments, the throttling pressure regulating device 9 includes a first valve core 91, the first channel 81 and / or the second channel 82 includes a third channel 83 and a fourth channel 84 connected to each other, the inner diameter of the third channel 83 is smaller than the inner diameter of the fourth channel 84, and the third channel 83 is located upstream of the fourth channel 84 along the direction of airflow, the first valve core 91 is located in the third channel 83 and the fourth channel 84 and can move in the third channel 83 and the fourth channel 84, a channel for throttling is formed between the outer peripheral wall of the first valve core 91 and the inner peripheral wall of the third channel 83, one axial end of the first valve core 91 is opposite to the direction of airflow so as to withstand the pressure of the airflow, when the gas pressure is relatively large, the length of the shaft section of the first valve core 91 entering the fourth channel 84 is relatively long, and the length of the shaft section located in the third channel 83 is relatively short; when the gas pressure is relatively small, the length of the shaft section of the first valve core 91 entering the fourth channel 84 is relatively short, and the length of the shaft section located in the third channel 83 is relatively long.

[0120] In the initial stage of starting a compressor with prior art, because the back pressure exhaust pressure and back pressure have not yet been established, the gas force generated by the initial compression pushes the moving disc apart, resulting in an increase in the gap, leakage in the pump body, and invalid compression, making it impossible to quickly establish an intake and exhaust pressure difference. After the pressure difference is established, the pressure on the back of the moving disc is also established, but most of the back pressure sources in the prior art are introduced into the back pressure chamber from the intermediate compression chamber, which is only suitable for applications with relatively fixed working conditions and cannot be suitable for a wider range of working conditions. In order to solve the above series of problems, the multi-channel back pressure supply and pressure regulation structure of the present application is provided. At the initial stage of starting the compressor, one or more back pressure supply channels are set up on the moving disc, and pressure is drawn from the low-pressure or medium-pressure compression chamber into the back pressure chamber to provide back pressure at the initial stage of compression, so that the moving disc is tightly attached to the static disc at the initial stage of starting the compressor, reducing internal leakage, quickly generating effective compression, and quickly establishing an intake and exhaust pressure difference. After the compressor starts normally and establishes normal exhaust pressure, back pressure is provided from the medium-pressure chamber, high-pressure chamber, or exhaust chamber through another one or more channels. During initial startup, the channel providing the initial back pressure from the low- or medium-pressure compression chamber is closed, switching to the supply pressure channel connecting the higher-pressure compression chamber or exhaust chamber to the back pressure chamber. This allows the compressor to adapt to a wider range of operating conditions after startup. A dynamic flow control valve is also installed in the channel connecting the exhaust chamber to the back pressure chamber to further increase the back pressure adjustment range. A back pressure relief channel is also installed on the bracket. When the back pressure is excessive, it is released from this channel to the low-pressure side, thus ensuring the dynamic balance and stability of the back pressure and achieving stable operation of the compressor.

[0121] The working principle of the pressure regulating throttle valve (i.e., throttling pressure regulating device) of the present invention is as follows:

[0122] When the exhaust pressure is not high, the valve core throttling pin (or valve core or throttling pin, the same throughout) is close to the left (as shown in state 1 in the figure). At this time, the spiral throttling channel is longer and the throttling effect is greater, obtaining a small back pressure that is adapted to the exhaust pressure to push the moving plate closer to the stationary plate. When the exhaust pressure increases, the throttling valve core overcomes the elastic force of the spring under the action of the exhaust pressure and gradually moves to the right (state 2 in the figure). At this time, the spiral throttling channel becomes shorter and the throttling effect decreases, obtaining a larger back pressure value that is adapted to the larger exhaust pressure to push the moving plate closer to the stationary plate. Maintain stable operation of the moving plate. Through this structure, the compressor can adapt to a wider range of operating conditions and improve the application field of the compressor.

[0123] Example 1:

[0124] like Figures 1 to 1-6, a channel 1 is set on the moving disc from the low-pressure compression chamber area to the medium-pressure compression chamber area, connecting the compression chamber and the back-pressure chamber respectively. A one-way valve is set on the channel, which only allows the refrigerant to enter the back-pressure chamber from the compression chamber, and the refrigerant cannot flow back to the compressor chamber from the channel. This channel ensures that the initial back pressure can be provided at the beginning of the compressor startup, reducing leakage at the beginning of startup and reducing invalid compression at the beginning of startup. However, after the compressor starts, with the continuous compression of the gas, the exhaust pressure gradually increases, and the axial force of the gas on the front of the moving disc also increases. At this time, the required balancing force back pressure must also be increased to ensure that the moving disc runs closely against the moving disc. At this time, the back pressure provided by channel 1 is no longer sufficient to balance the gas force on the front of the moving disc. It is necessary to open a channel at a higher-pressure compression chamber position (not shown in the figure) to introduce a higher pressure to the back-pressure chamber to balance the higher gas force at this time. Preferably, a second channel connected to the back-pressure chamber is opened in the high-pressure chamber (exhaust chamber) to meet higher back-pressure requirements, and a throttling pressure regulating valve is set on the channel to provide appropriate back-pressure from the high-pressure chamber to the back-pressure chamber. The throttling pressure regulating valve is set so that the back-pressure is equal to or slightly greater than the axial force of the compressed gas, so as to ensure that the moving disk runs closely against the stationary disk. When the exhaust pressure of the compressor is relatively high, the back-pressure required to balance the axial force of the gas is also large. At this time, the gas force in the high-pressure chamber pushes the valve core to the right, the spiral path of the valve core throttling gradually becomes shorter, the throttling cross-section gradually becomes larger, and the throttling effect gradually decreases. The more high-pressure gas enters the back-pressure chamber, the greater the back-pressure provided, and eventually reaches a level equal to or slightly greater than the axial force of the gas.

[0125] At the same time, in order to prevent the back pressure from being too large, especially when the compressor temporarily changes its operating conditions or the exhaust pressure increases abnormally, the back pressure becomes too large, and it is necessary to relieve the back pressure. Preferably, one or more first pressure relief channels 31 connecting the back pressure chamber and the low pressure chamber are provided on the bracket, and a one-way valve or a throttling regulating valve is provided on the channel to keep the back pressure within a reasonable dynamic balance range, thereby ensuring that the moving disc can operate more stably.

[0126] Example 1, as Figures 1 to 1-3 , the throttling and pressure regulating device is set to a structure without a valve body shell;

[0127] Example 2, as Figures 2 to 2-3 , the throttling and pressure regulating device is arranged on the bracket, and a filter is arranged on the pressure supply channel;

[0128] Example 3, as Figures 3 to 3-3 , the throttling and pressure regulating device is set on the bracket, and the pressure relief valve adopts a one-way ball valve;

[0129] Example 4, as Figures 4 to 4-3 , the throttling and pressure regulating device is arranged on the cover body (also called end cover or front cover), and the valve core is an external spiral groove;

[0130] Example 5, as Figures 5 to 5-3 , the throttling and pressure regulating device is arranged on the cover body, the valve core is a polished rod, and the valve body shell is provided with an inner spiral groove;

[0131] Example 6, as Figures 6 to 6-3 , the throttling and pressure regulating device is installed on the bracket, and a filter is added to the channel;

[0132] Example 7, as Figures 7 to 7-3 The throttling and pressure regulating device is installed on the bracket, a filter is added to the channel, and a through groove is set at the tail of the valve body shell;

[0133] Example 8, as Figures 8 to 8-3 , an inner spiral groove is provided on the valve body shell, and the valve body is installed on the bracket;

[0134] Example 9, as Figures 9 to 9-3 The valve body is set to a pre-assembled component structure, and the valve core and valve body shell are not provided with a spiral groove structure, but a polished rod clearance fit structure;

[0135] Example 10, as Figures 10 to 10-3 , the pressure relief valve is configured as a spiral cylindrical pin structure;

[0136] Example 11, as Figures 11 to 11-3 , without initial compression chamber pressure supply channel and ball valve;

[0137] Example 12, as Figures 12 to 12-3 , there is no initial compression chamber pressure supply channel and ball valve, and the pressure relief valve is a spiral throttling pin;

[0138] Example 13, as Figures 13 to 13-3 , there is an initial compression chamber pressure supply channel, but no one-way ball valve;

[0139] Example 14, as Figures 14 to 14-3 , there is no initial compression chamber pressure supply channel and one-way ball valve, and the pressure is released to the low-pressure compression chamber, not to the low-pressure side.

[0140] One or more channels 1 are provided on the moving disc from the low-pressure compression chamber area to the medium-pressure compression chamber area, connecting the compression chamber and the back-pressure chamber respectively. A one-way valve is provided on the channel, which only allows the refrigerant to fill the compression chamber and enter the back-pressure chamber, and the refrigerant cannot flow back to the compressor chamber from the channel. This channel ensures that the initial back pressure can be provided at the beginning of the compressor startup, reducing leakage at the beginning of startup and reducing ineffective compression at the beginning of startup. However, after the compressor is started, as the gas is continuously compressed, the exhaust pressure gradually increases, and the axial force of the gas on the front of the moving disc also increases. At this time, the required balancing force back pressure must also be increased to ensure that the moving disc operates closely against the moving disc. At this time, the back pressure provided by channel 1 is no longer sufficient to balance the gas force on the front of the moving disc. It is necessary to open a channel at a higher pressure compression chamber position (not shown in the figure) to introduce a higher pressure to the back-pressure chamber to balance the higher gas force at this time. In this embodiment, the back-pressure induction and pressure regulating throttle valve is provided on the bracket, and a filter is provided on the pressure induction channel.

[0141] The basic principles of the following other embodiments are the same as those of this embodiment and will not be repeated hereafter.

[0142] In some embodiments, an outer spiral groove is provided on the outer peripheral wall of the first valve core 91, and / or an inner spiral groove is provided on the inner peripheral wall of the third channel 83 to form the throttling channel. When the gas pressure is relatively large, the length of the axial section of the first valve core 91 located in the third channel 83 is relatively short, the length of throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the axial section of the first valve core 91 located in the third channel 83 is relatively long, the length of throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

[0143] In some embodiments, there is a first gap between the outer circumferential wall of the first valve core 91 and the inner circumferential wall of the third channel 83 to form the throttling channel. When the gas pressure is relatively large, the length of the axial section of the first valve core 91 located in the third channel 83 is relatively short, the length of the throttling through the first gap is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the axial section of the first valve core 91 located in the third channel 83 is relatively long, the length of the throttling through the first gap is relatively long, and the throttling opening is relatively small.

[0144] In some embodiments, when the axial end of the first valve core 91 is not subjected to gas pressure, the first valve core 91 is entirely located in the third channel 83 or most of it is located in the third channel 83. When the gas pressure borne by the axial end of the first valve core 91 increases, the length of the first valve core 91 entering the fourth channel 84 increases, resulting in a decrease in the throttling effect; when the gas pressure borne by the axial end of the first valve core 91 decreases, the length of the first valve core 91 entering the fourth channel 84 decreases, resulting in an increase in the throttling effect.

[0145] In some embodiments, a first elastic member 92 is further included, one end of which is fixed and the other end is connected to the first valve core 91, and can provide the first valve core 91 with an elastic restoring force to move toward the third channel 83. The other end of the first elastic member 92 is connected to the end of the first valve core 91 opposite to the axial end.

[0146] In some embodiments, a first accommodating groove 93 is defined inside the first valve core 91 , a portion of the first elastic member 92 is passed through the first accommodating groove 93 , and the other end of the first elastic member 92 is fixedly connected to or abuts against the bottom of the first accommodating groove 93 .

[0147] In some embodiments, a first annular boss 911 extending radially outward is formed at the other axial end of the first valve core 91, and a first step 87 is formed at the junction of the third channel 83 and the fourth channel 84. The first annular boss 911 can be matched and engaged with the first step 87 to form a limit; and / or, a first limit member 88 is provided at the end of the fourth channel 84 away from the third channel 83, and the first limit member 88 is fixedly connected to the cover body 4 or the bracket 3, and one end of the first elastic member 92 is fixedly connected to the first limit member 88. The first limit member 88 is also provided with a through hole for accommodating the passage of gas.

[0148] In some embodiments, the throttling pressure regulating device 9 includes a first valve housing 94 and a second valve core 95. The first valve housing 94 is located in the first channel 81 and / or the second channel 82. The first valve housing 94 has a first internal channel inside. The second valve core 95 is arranged in the first internal channel and can move in the first internal channel. The first internal channel includes a fifth channel 85 and a sixth channel 86 connected to each other. The inner diameter of the fifth channel 85 is smaller than that of the sixth channel 86, and the fifth channel 85 is located upstream of the sixth channel 86 along the flow direction of the airflow. A channel for throttling is formed between the outer circumferential wall of the second valve core 95 and the inner circumferential wall of the first valve housing 94. One axial end of the second valve core 95 is opposite to the direction of airflow so as to withstand the pressure of the airflow. When the gas pressure is relatively large, the length of the shaft section of the second valve core 95 entering the sixth channel 86 is relatively long, and the length of the shaft section located in the fifth channel 85 is relatively short; when the gas pressure is relatively small, the length of the shaft section of the second valve core 95 entering the sixth channel 86 is relatively short, and the length of the shaft section located in the fifth channel 85 is relatively long.

[0149] In some embodiments, an outer spiral groove is provided on the outer circumferential wall of the second valve core 95, and / or an inner spiral groove is provided on the inner circumferential wall of the fifth channel 85 to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the second valve core 95 entering the sixth channel 86 is relatively long, and the length of the shaft section located in the fifth channel 85 is relatively short. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the shaft section of the second valve core 95 entering the sixth channel 86 is relatively short, and the length of the shaft section located in the fifth channel 85 is relatively long. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

[0150] In some embodiments, a second gap is provided between the outer peripheral wall of the second valve core 95 and the inner peripheral wall of the fifth channel 85 to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the second valve core 95 entering the sixth channel 86 is relatively long, and the length of the shaft section located in the fifth channel 85 is relatively short. The length throttling through the second gap is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively small, the length of the shaft section of the second valve core 95 entering the sixth channel 86 is relatively short, and the length of the shaft section located in the fifth channel 85 is relatively long. The length throttling through the second gap is relatively long, and the throttling opening is relatively small.

[0151] In some embodiments, when the axial end of the second valve core 95 is not subjected to gas pressure, the second valve core 95 is entirely located in the fifth channel 85 or most of it is located in the fifth channel 85; when the axial end of the second valve core 95 is subjected to increased gas pressure, the length of the second valve core 95 entering the sixth channel 86 increases, resulting in a decrease in the throttling effect; when the axial end of the second valve core 95 is subjected to decreased gas pressure, the length of the second valve core 95 entering the sixth channel 86 decreases, resulting in an increase in the throttling effect.

[0152] In some embodiments, a second elastic member 96 is further included, one end of which is fixed to the first valve housing 94 and the other end is connected to the second valve core 95, and can provide an elastic restoring force for the second valve core 95 to move toward the fifth channel 85, and the other end of the second elastic member 96 is connected to the end of the second valve core 95 opposite to the axial end.

[0153] In some embodiments, a second accommodating groove 97 is defined inside the second valve core 95 , a portion of the second elastic member 96 is passed through the second accommodating groove 97 , and the other end of the second elastic member 96 is fixedly connected to or abuts against the bottom of the second accommodating groove 97 .

[0154] In some embodiments, a second annular boss 951 extending radially outward is formed at the other axial end of the second valve core 95, and a second step 89 is formed at the junction of the fifth channel 85 and the sixth channel 86. The second annular boss 951 can be matched and engaged with the second step 89 to form a limit; and / or, a second limit member 810 is provided at the end of the first valve housing 94 located downstream in the direction of air flow, and the second limit member 810 is fixedly connected to the first valve housing 94, and one end of the second elastic member 96 is fixedly connected to the second limit member 810, and the second limit member 810 is also provided with a through hole for accommodating gas passage.

[0155] In some embodiments, a first pressure relief channel 31 is further provided inside the bracket 3, and a pressure relief regulating valve 10 is provided in the first pressure relief channel 31. One end of the first pressure relief channel 31 is connected to the back pressure chamber 5, and the other end is connected to the outside of the bracket 3 (the suction side of the scroll compressor). The pressure relief regulating valve 10 can throttle the inside of the first pressure relief channel 31 to adjust the flow rate in the first pressure relief channel 31.

[0156] The present invention sets a pressure relief regulating valve in the first pressure relief channel on the bracket. The pressure relief regulating valve can achieve stable pressure relief or adjust the flow rate according to the pressure of the incoming air flow. When the incoming flow pressure is large, the flow rate passing through is automatically controlled to be large, which can make the back pressure chamber pressure high and release a large pressure to it, thereby preventing the back pressure chamber from being too high and causing the movable disc to overturn or wear, and preventing the movable disc from being pushed by the exhaust pressure. When the incoming flow pressure is small, the flow rate passing through is automatically controlled to be small, which can make the back pressure chamber pressure small and release a small pressure to the back pressure chamber, thereby preventing the back pressure chamber from being too small and causing gas leakage between the movable disc and the static disc. Therefore, the pressure relief regulating structure of the present invention can automatically adjust the degree of pressure relief according to the size of the back pressure chamber pressure, which can prevent the movable disc from overturning or wearing while also preventing gas leakage between the movable disc and the static disc.

[0157] The working principle of the pressure relief valve of the present invention:

[0158] When the back pressure is low, the valve core throttling pin is close to the left (as shown in the figure below). At this time, the spiral throttling channel is longer, the throttling effect is greater, and the back pressure is slowly released to the low-pressure side, so that the back pressure chamber is dynamically balanced. When the back pressure increases, the throttling valve core overcomes the elastic force of the spring under the action of the back pressure and gradually moves to the right. At this time, the spiral throttling channel becomes shorter, the throttling effect is reduced, and the back pressure relief flow rate increases, promoting the dynamic balance and stability of the back pressure and maintaining the stable operation of the dynamic disc. Through this structure, the compressor can adapt to a wider range of operating conditions and expand the application field of the compressor.

[0159] The basic principles of the following other embodiments are the same as those of this embodiment and will not be repeated hereafter.

[0160] In some embodiments, the pressure relief regulating valve 10 can automatically adjust the size of the throttling flow according to the size of the incoming gas pressure in the first pressure relief channel 31. When the gas pressure is relatively large, its throttling opening is relatively large, and a relatively large flow of gas can be allowed to pass through. When the gas pressure is relatively small, its throttling opening is relatively small, and a relatively small flow of gas can be allowed to pass through, so as to relieve the pressure in the back pressure chamber 5 to the outside of the bracket 3 (the suction side of the scroll compressor).

[0161] In some embodiments, the pressure relief regulating valve 10 includes a second valve housing 101 and a third valve core 102. The second valve housing 101 is located in the first pressure relief channel 31. The interior of the second valve housing 101 has a second internal channel. The third valve core 102 is disposed in the second internal channel and can move in the second internal channel. The second internal channel includes a seventh channel 103 and an eighth channel 104 connected to each other. The inner diameter of the seventh channel 103 is smaller than that of the eighth channel 104, and the seventh channel 103 is located upstream of the eighth channel 104 along the direction of airflow. A channel for throttling is formed between the outer circumferential wall of the third valve core 102 and the inner circumferential wall of the second valve housing 101. One axial end of the third valve core 102 is opposite to the direction of airflow so as to withstand the pressure of the airflow. When the gas pressure is relatively large, the length of the shaft section of the third valve core 102 entering the eighth channel 104 is relatively long, and the length of the shaft section located in the seventh channel 103 is relatively short. When the gas pressure is relatively small, the length of the shaft section of the third valve core 102 entering the eighth channel 104 is relatively short, and the length of the shaft section located in the seventh channel 103 is relatively long.

[0162] In some embodiments, an outer spiral groove is provided on the outer peripheral wall of the third valve core 102, and / or an inner spiral groove is provided on the inner peripheral wall of the seventh channel 103 to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the third valve core 102 entering the eighth channel 104 is relatively long, and the length of the shaft section located in the seventh channel 103 is relatively short. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the shaft section of the third valve core 102 entering the eighth channel 104 is relatively short, and the length of the shaft section located in the seventh channel 103 is relatively long. The length throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

[0163] In some embodiments, there is a third gap between the outer circumferential wall of the third valve core 102 and the inner circumferential wall of the seventh channel 103 to form the throttling channel. When the gas pressure is relatively large, the length of the shaft section of the third valve core 102 entering the eighth channel 104 is relatively long, and the length of the shaft section located in the seventh channel 103 is relatively short. The length of throttling through the third gap is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively small, the length of the shaft section of the third valve core 102 entering the eighth channel 104 is relatively short, and the length of the shaft section located in the seventh channel 103 is relatively long. The length of throttling through the third gap is relatively long, and the throttling opening is relatively small.

[0164] In some embodiments, when the axial end of the third valve core is not subjected to gas pressure, its spiral groove structure is entirely located in the third channel or most of it is located in the third channel. When the axial end of the third valve core is subjected to increased gas pressure, the length of the third valve core entering the fourth channel increases, resulting in a decrease in the throttling effect; when the axial end of the third valve core is subjected to decreased gas pressure, the length of the third valve core entering the fourth channel decreases, resulting in an increase in the throttling effect.

[0165] In some embodiments, a third elastic member 105 is further included, one end of which is fixed to the second valve housing 101 and the other end is connected to the third valve core 102, and can provide an elastic restoring force for the third valve core 102 to move toward the seventh channel 103, and the other end of the third elastic member 105 is connected to the end of the third valve core 102 opposite to the axial end.

[0166] In some embodiments, a third accommodating groove 106 is opened inside the third valve core 102, a partial section of the third elastic member 105 is passed through the third accommodating groove 106, and the other end of the third elastic member 105 is fixedly connected or abutted against the bottom of the third accommodating groove 106.

[0167] In some embodiments, the pressure relief regulating valve 10 is a columnar throttling spiral pin, and a spiral throttling groove is provided on its outer peripheral wall. The first pressure relief channel 31 is a columnar channel with a constant cross-section. The throttling spiral pin is arranged in the first pressure relief channel 31, which can achieve a fixed throttling effect on the fluid.

[0168] In some embodiments, a first one-way valve 107 and a fourth elastic member 108 are further provided in the first pressure relief channel 31. One end of the fourth elastic member 108 is connected to the pressure relief regulating valve 10, and the other end is connected to the first one-way valve 107. The first one-way valve 107 only allows gas to flow out from the back pressure chamber 5 toward the outside of the bracket 3.

[0169] In some embodiments, a second pressure relief channel 16 is provided on the movable disc 1, one end of the second pressure relief channel 16 is connected to the low-pressure chamber in the compression chamber 11, and the other end is connected to the back-pressure chamber 5, so that the pressure in the back-pressure chamber 5 can be relieved to the low-pressure chamber. The compression chamber 11 includes a low-pressure chamber, a medium-pressure chamber and a high-pressure chamber, which are respectively a high-pressure chamber, a medium-pressure chamber and a low-pressure chamber in order of pressure from large to small. The pressure of the high-pressure chamber is equal to the pressure of the exhaust chamber 7.

[0170] In some embodiments, an initial back pressure supply channel 12 is provided on the moving disk 1, one end of the initial back pressure supply channel 12 is connected to the low pressure chamber or the medium pressure chamber in the compression chamber 11, and the other end is connected to the back pressure chamber 5, so that the pressure in the low pressure chamber or the medium pressure chamber can be released into the back pressure chamber 5. The compression chamber 11 includes a low pressure chamber, a medium pressure chamber and a high pressure chamber, which are respectively a high pressure chamber, a medium pressure chamber and a low pressure chamber in order of pressure from large to small. The pressure of the high pressure chamber is equal to the pressure of the exhaust chamber 7.

[0171] The present invention also uses an initial back pressure supply channel to guide the medium pressure or low pressure in the compression chamber to the back pressure chamber through the initial back pressure supply channel when there is not enough exhaust gas at the initial stage of the compressor startup, thereby providing back pressure to the moving plate, effectively solving the problem that when the compressor is just started, the exhaust pressure and back pressure have not yet been established, the moving plate and the static plate are pushed apart by the reaction force of the gas compression force, the gap becomes larger, the leakage increases instantly, an invalid compression process is formed, and the suction and exhaust pressure difference cannot be established quickly; that is, it solves the problem of invalid compression when the compressor is started, and reduces the time for establishing the suction and exhaust pressure difference; and by arranging a one-way valve structure in the initial back pressure supply channel, it can reduce the repeated compression process caused by the back pressure chamber bleeding into the compression chamber.

[0172] In some embodiments, a second one-way valve 13 is further provided in the initial back pressure supply channel 12, and the second one-way valve only allows the fluid to flow from the low pressure chamber or the medium pressure chamber to the back pressure chamber 5; and / or, a second throttle valve 14 is further provided in the initial back pressure supply channel 12, and the second throttle valve 14 is a columnar throttling spiral pin, and a spiral throttling groove is provided on its outer peripheral wall, and the second throttle valve 14 can achieve a fixed throttling effect on the fluid.

[0173] In some embodiments, when a second one-way valve 13 and a second throttle valve 14 are included at the same time, the second one-way valve 13 is also a one-way ball valve, and a fifth elastic member 15 is also provided in the initial back pressure supply channel 12, and one end of the fifth elastic member 15 is connected to the second throttle valve 14, and the other end is connected to the second one-way valve 13.

[0174] In some embodiments, the second channel 82 includes a second channel 1 821 and a second channel 2 822, the second channel 1 821 extends along the axial direction of the bracket 3, the central axis of the second channel 2 822 forms an angle between 0 and 90 degrees with the axis of the bracket 3, one end of the second channel 1 821 is located at the axial end of the bracket 3 opposite to the cover body 4, and is connected to the first channel 81, the other end of the second channel 1 821 is connected to one end of the second channel 2 822, and the other end of the second channel 2 822 extends to connect with the back pressure chamber 5.

[0175] In some embodiments, when the throttling pressure regulating device 9 includes a first valve housing 94 and a second valve core 95, and the first valve housing 94 is located in the second channel 82, a notch 941 is provided on the first valve housing 94 at a position where it connects with the second channel 822.

[0176] The present invention also provides an air conditioner, comprising the scroll compressor capable of automatically adjusting back pressure as described in any of the preceding items.

[0177] 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 shall be included within the scope of protection of the present invention. The above description is merely a preferred embodiment of the present invention. It should be noted that those skilled in the art can make various improvements and variations without departing from the technical principles of the present invention, and such improvements and variations shall also be considered within the scope of protection of the present invention.

Claims

1. A scroll compressor capable of automatically adjusting back pressure, characterized in that: include: A moving disc (1), a stationary disc (2), a bracket (3) and a cover body (4), wherein a back pressure chamber (5) is provided inside the bracket (3) to provide back pressure to the moving disc (1), the moving disc (1) and the stationary disc (2) are engaged to form a compression chamber (11), an exhaust port (6) is provided on the stationary disc (2), the cover body (4) is connected to the stationary disc (2), an exhaust chamber (7) is provided inside the cover body (4), one end of the exhaust port (6) is communicated with the compression chamber (11), and the other end is communicated with the exhaust chamber (7); The cover body (4) is further provided with an exhaust channel (41) and a first channel (81), and the bracket (3) is provided with a second channel (82), one end of the exhaust channel (41) is communicated with the exhaust chamber (7), and the other end can be communicated with the outside of the cover body (4) for exhaust, one end of the first channel (81) is communicated with the exhaust channel (41), and the other end is communicated with one end of the second channel (82), and the other end of the second channel (82) is communicated with the back pressure chamber (5), and a throttling pressure regulating device (9) is provided in the first channel (81) and / or the second channel (82), and the throttling pressure regulating device (9) can automatically adjust the size of the throttling flow according to the size of the incoming gas pressure; When the gas pressure is relatively high, the throttling opening of the throttling pressure regulating device (9) is relatively large, allowing a relatively large flow of gas to pass through; when the gas pressure is relatively low, the throttling opening of the throttling pressure regulating device (9) is relatively small, allowing a relatively small flow of gas to pass through; The throttling pressure regulating device (9) includes a first valve core (91), the first channel (81) and / or the second channel (82) include a third channel (83) and a fourth channel (84) connected to each other, the inner diameter of the third channel (83) is smaller than the inner diameter of the fourth channel (84), and the third channel (83) is located upstream of the fourth channel (84) along the flow direction of the airflow, the first valve core (91) is located in the third channel (83) and the fourth channel (84) and can move in the third channel (83) and the fourth channel (84), and the first valve core ( A channel for throttling is formed between the outer peripheral wall of the valve core (91) and the inner peripheral wall of the third channel (83), and one axial end of the first valve core (91) is opposite to the direction of the airflow so as to withstand the pressure of the airflow. When the gas pressure is relatively high, the length of the shaft section of the first valve core (91) entering the fourth channel (84) is relatively long, and the length of the shaft section located in the third channel (83) is relatively short; when the gas pressure is relatively low, the length of the shaft section of the first valve core (91) entering the fourth channel (84) is relatively short, and the length of the shaft section located in the third channel (83) is relatively long.

2. The scroll compressor capable of automatically adjusting back pressure according to claim 1, characterized in that: An outer spiral groove is provided on the outer peripheral wall of the first valve core (91), and / or an inner spiral groove is provided on the inner peripheral wall of the third channel (83), so as to form the throttling channel. When the gas pressure is relatively high, the length of the shaft section of the first valve core (91) located in the third channel (83) is relatively short, the length of throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large; when the gas pressure is relatively low, the length of the shaft section of the first valve core (91) located in the third channel (83) is relatively long, the length of throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

3. The scroll compressor capable of automatically adjusting back pressure according to claim 1, characterized in that: A first gap is provided between the outer peripheral wall of the first valve core (91) and the inner peripheral wall of the third channel (83) to form the throttling channel. When the gas pressure is relatively high, the length of the shaft section of the first valve core (91) in the third channel (83) is relatively short, the length of the throttling through the first gap is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively low, the length of the shaft section of the first valve core (91) in the third channel (83) is relatively long, the length of the throttling through the first gap is relatively long, and the throttling opening is relatively small.

4. The scroll compressor capable of automatically adjusting back pressure according to claim 1, characterized in that: When the axial end of the first valve core (91) is not subjected to gas pressure, the first valve core (91) is entirely located in the third channel (83) or most of it is located in the third channel (83). When the gas pressure borne by the axial end of the first valve core (91) increases, the length of the first valve core (91) entering the fourth channel (84) increases, resulting in a decrease in the throttling effect; when the gas pressure borne by the axial end of the first valve core (91) decreases, the length of the first valve core (91) entering the fourth channel (84) decreases, resulting in an increase in the throttling effect.

5. The scroll compressor capable of automatically adjusting back pressure according to claim 1, characterized in that: The invention also includes a first elastic member (92), one end of which is fixed and the other end is connected to the first valve core (91), and can provide the first valve core (91) with an elastic restoring force to move in the direction of the third channel (83), and the other end of the first elastic member (92) is connected to the end of the first valve core (91) opposite to the axial end.

6. The scroll compressor capable of automatically adjusting back pressure according to claim 5, characterized in that: A first accommodating groove (93) is provided inside the first valve core (91), a portion of the first elastic member (92) is passed through the first accommodating groove (93), and the other end of the first elastic member (92) is fixedly connected to or abuts against the bottom of the first accommodating groove (93).

7. The scroll compressor capable of automatically adjusting back pressure according to claim 5, characterized in that: A first annular boss (911) extending radially outward is formed at the other axial end of the first valve core (91), and a first step (87) is formed at the junction of the third channel (83) and the fourth channel (84), and the first annular boss (911) can be matched and engaged with the first step (87) to form a limit; and / or, a first limit member (88) is provided at the end of the fourth channel (84) away from the third channel (83), and the first limit member (88) is fixedly connected to the cover body (4) or the bracket (3), and one end of the first elastic member (92) is fixedly connected to the first limit member (88), and the first limit member (88) is also provided with a through hole for accommodating gas passing through.

8. The scroll compressor capable of automatically adjusting back pressure according to claim 1, characterized in that: A first pressure relief channel (31) is further provided inside the bracket (3), and a pressure relief regulating valve (10) is provided in the first pressure relief channel (31). One end of the first pressure relief channel (31) is connected to the back pressure chamber (5), and the other end is connected to the suction side of the scroll compressor. The pressure relief regulating valve (10) can throttle the inside of the first pressure relief channel (31) to adjust the flow rate in the first pressure relief channel (31).

9. The scroll compressor capable of automatically adjusting back pressure according to claim 8, characterized in that: The pressure relief regulating valve (10) is capable of automatically adjusting the size of the throttling flow rate according to the size of the incoming gas pressure in the first pressure relief channel (31). When the gas pressure is relatively large, the throttling opening is relatively large, allowing a relatively large flow of gas to pass through. When the gas pressure is relatively small, the throttling opening is relatively small, allowing a relatively small flow of gas to pass through, so as to relieve the pressure in the back pressure chamber (5) to the suction side of the scroll compressor.

10. The scroll compressor capable of automatically adjusting back pressure according to claim 9, characterized in that: The pressure relief regulating valve (10) comprises a second valve housing (101) and a third valve core (102), wherein the second valve housing (101) is located in the first pressure relief channel (31), the interior of the second valve housing (101) comprises a second internal channel, the third valve core (102) is arranged in the second internal channel and is movable in the second internal channel, the second internal channel comprises a seventh channel (103) and an eighth channel (104) connected to each other, the inner diameter of the seventh channel (103) is smaller than that of the eighth channel (104), and the seventh channel (103) is located upstream of the eighth channel (104) along the direction of airflow. A throttling channel is formed between the outer peripheral wall of the third valve core (102) and the inner peripheral wall of the second valve housing (101). One axial end of the third valve core (102) is opposite to the direction of the airflow so as to withstand the pressure of the airflow. When the gas pressure is relatively large, the length of the shaft section of the third valve core (102) entering the eighth channel (104) is relatively long, and the length of the shaft section located in the seventh channel (103) is relatively short. When the gas pressure is relatively small, the length of the shaft section of the third valve core (102) entering the eighth channel (104) is relatively short, and the length of the shaft section located in the seventh channel (103) is relatively long.

11. The scroll compressor capable of automatically adjusting back pressure according to claim 10, characterized in that: An outer spiral groove is provided on the outer peripheral wall of the third valve core (102), and / or an inner spiral groove is provided on the inner peripheral wall of the seventh channel (103), so as to form the throttling channel. When the gas pressure is relatively high, the length of the shaft section of the third valve core (102) entering the eighth channel (104) is relatively long, and the length of the shaft section located in the seventh channel (103) is relatively short. The length of throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively low, the length of the shaft section of the third valve core (102) entering the eighth channel (104) is relatively short, and the length of the shaft section located in the seventh channel (103) is relatively long. The length of throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

12. The scroll compressor capable of automatically adjusting back pressure according to claim 10, characterized in that: A third gap is provided between the outer peripheral wall of the third valve core (102) and the inner peripheral wall of the seventh channel (103) to form the throttling channel. When the gas pressure is relatively high, the length of the shaft section of the third valve core (102) entering the eighth channel (104) is relatively long, and the length of the shaft section located in the seventh channel (103) is relatively short. The length of the throttling through the third gap is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively low, the length of the shaft section of the third valve core (102) entering the eighth channel (104) is relatively short, and the length of the shaft section located in the seventh channel (103) is relatively long. The length of the throttling through the third gap is relatively long, and the throttling opening is relatively small.

13. The scroll compressor capable of automatically adjusting back pressure according to claim 10, characterized in that: The third elastic member (105) further comprises a third elastic member (105), one end of which is fixed to the second valve housing (101) and the other end of which is connected to the third valve core (102), and is capable of providing an elastic restoring force for the third valve core (102) to move in the direction of the seventh channel (103), and the other end of the third elastic member (105) is connected to the end of the third valve core (102) opposite to the axial end.

14. The scroll compressor capable of automatically adjusting back pressure according to claim 13, characterized in that: A third accommodating groove (106) is provided inside the third valve core (102), a portion of the third elastic member (105) is passed through the third accommodating groove (106), and the other end of the third elastic member (105) is fixedly connected to or abuts against the bottom of the third accommodating groove (106).

15. The scroll compressor capable of automatically adjusting back pressure according to claim 8, characterized in that: The pressure relief regulating valve (10) is a columnar throttling spiral pin, and a spiral throttling groove is provided on its outer peripheral wall. The throttling spiral pin is arranged in the first pressure relief channel (31) and can achieve a fixed throttling effect on the fluid.

16. The scroll compressor capable of automatically adjusting back pressure according to claim 15, characterized in that: A first one-way valve (107) and a fourth elastic member (108) are also provided in the first pressure relief channel (31). One end of the fourth elastic member (108) is connected to the pressure relief regulating valve (10), and the other end is connected to the first one-way valve (107). The first one-way valve (107) only allows gas to flow out from the back pressure chamber (5) toward the suction side of the scroll compressor.

17. The scroll compressor capable of automatically adjusting back pressure according to claim 1, characterized in that: A second pressure relief channel (16) is provided on the movable disc (1), one end of the second pressure relief channel (16) is communicated with the low-pressure chamber in the compression chamber (11), and the other end is communicated with the back-pressure chamber (5), so as to be able to relieve the pressure in the back-pressure chamber (5) into the low-pressure chamber. The compression chamber (11) includes a low-pressure chamber, a medium-pressure chamber and a high-pressure chamber, which are respectively a high-pressure chamber, a medium-pressure chamber and a low-pressure chamber in descending order of pressure. The pressure of the high-pressure chamber is equal to the pressure of the exhaust chamber (7).

18. The scroll compressor capable of automatically adjusting back pressure according to any one of claims 1 to 17, characterized in that: An initial back pressure supply channel (12) is provided on the movable disc (1), one end of the initial back pressure supply channel (12) is communicated with the low pressure chamber or the medium pressure chamber in the compression chamber (11), and the other end is communicated with the back pressure chamber (5), so as to be able to release the pressure in the low pressure chamber or the medium pressure chamber into the back pressure chamber (5). The compression chamber (11) includes a low pressure chamber, a medium pressure chamber and a high pressure chamber, which are respectively a high pressure chamber, a medium pressure chamber and a low pressure chamber in descending order of pressure. The pressure of the high pressure chamber is equal to the pressure of the exhaust chamber (7).

19. The scroll compressor capable of automatically adjusting back pressure according to claim 18, characterized in that: A second one-way valve (13) is also provided in the initial back pressure supply channel (12), and the second one-way valve only allows the fluid to flow from the low pressure chamber or the medium pressure chamber to the back pressure chamber (5); and / or, a second throttle valve (14) is also provided in the initial back pressure supply channel (12), and the second throttle valve (14) is a columnar throttling spiral pin, and a spiral throttling groove is provided on its outer peripheral wall, and the second throttle valve (14) can achieve a fixed throttling effect on the fluid.

20. The scroll compressor capable of automatically adjusting back pressure according to claim 19, characterized in that: When both the second one-way valve (13) and the second throttle valve (14) are included, the second one-way valve (13) is also a one-way ball valve, and a fifth elastic member (15) is further provided in the initial back pressure supply channel (12), one end of the fifth elastic member (15) is connected to the second throttle valve (14), and the other end is connected to the second one-way valve (13).

21. The scroll compressor capable of automatically adjusting back pressure according to any one of claims 1 to 17, characterized in that: The second channel (82) includes a second channel 1 (821) and a second channel 2 (822), wherein the second channel 1 (821) extends along the axial direction of the bracket (3), and the central axis of the second channel 2 (822) forms an angle between 0° and 90° with the axis of the bracket (3), one end of the second channel 1 (821) is located at the axial end of the bracket (3) opposite to the cover body (4), and is connected to the first channel (81), the other end of the second channel 1 (821) is connected to one end of the second channel 2 (822), and the other end of the second channel 2 (822) extends to be connected to the back pressure chamber (5).

22. A scroll compressor capable of automatically adjusting back pressure, characterized in that: A moving disc (1), a stationary disc (2), a bracket (3) and a cover body (4), wherein a back pressure chamber (5) is provided inside the bracket (3) to provide back pressure to the moving disc (1), the moving disc (1) and the stationary disc (2) are engaged to form a compression chamber (11), an exhaust port (6) is provided on the stationary disc (2), the cover body (4) is connected to the stationary disc (2), an exhaust chamber (7) is provided inside the cover body (4), one end of the exhaust port (6) is communicated with the compression chamber (11), and the other end is communicated with the exhaust chamber (7); The cover body (4) is further provided with an exhaust channel (41) and a first channel (81), and the bracket (3) is provided with a second channel (82), one end of the exhaust channel (41) is communicated with the exhaust chamber (7), and the other end can be communicated with the outside of the cover body (4) for exhaust, one end of the first channel (81) is communicated with the exhaust channel (41), and the other end is communicated with one end of the second channel (82), and the other end of the second channel (82) is communicated with the back pressure chamber (5), and a throttling pressure regulating device (9) is provided in the first channel (81) and / or the second channel (82), and the throttling pressure regulating device (9) can automatically adjust the size of the throttling flow according to the size of the incoming gas pressure; When the gas pressure is relatively high, the throttling opening of the throttling pressure regulating device (9) is relatively large, allowing a relatively large flow of gas to pass through; when the gas pressure is relatively low, the throttling opening of the throttling pressure regulating device (9) is relatively small, allowing a relatively small flow of gas to pass through; The throttling pressure regulating device (9) comprises a first valve housing (94) and a second valve core (95), wherein the first valve housing (94) is located in the first channel (81) and / or the second channel (82), the first valve housing (94) has a first internal channel inside, the second valve core (95) is arranged in the first internal channel and can move in the first internal channel, the first internal channel comprises a fifth channel (85) and a sixth channel (86) connected to each other, the inner diameter of the fifth channel (85) is smaller than that of the sixth channel (86), and the fifth channel (85) is located in the sixth channel (86) along the flow direction of the airflow. ), a channel for throttling is formed between the outer peripheral wall of the second valve core (95) and the inner peripheral wall of the first valve housing (94), and one axial end of the second valve core (95) is opposite to the direction of the airflow so as to withstand the pressure of the airflow. When the gas pressure is relatively large, the length of the shaft section of the second valve core (95) entering the sixth channel (86) is relatively long, and the length of the shaft section located in the fifth channel (85) is relatively short; when the gas pressure is relatively small, the length of the shaft section of the second valve core (95) entering the sixth channel (86) is relatively short, and the length of the shaft section located in the fifth channel (85) is relatively long.

23. The scroll compressor capable of automatically adjusting back pressure according to claim 22, characterized in that: An outer spiral groove is provided on the outer peripheral wall of the second valve core (95), and / or an inner spiral groove is provided on the inner peripheral wall of the fifth channel (85), so as to form the throttling channel. When the gas pressure is relatively high, the length of the shaft section of the second valve core (95) entering the sixth channel (86) is relatively long, and the length of the shaft section located in the fifth channel (85) is relatively short. The length of throttling through the outer spiral groove and / or the inner spiral groove is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively low, the length of the shaft section of the second valve core (95) entering the sixth channel (86) is relatively short, and the length of the shaft section located in the fifth channel (85) is relatively long. The length of throttling through the outer spiral groove and / or the inner spiral groove is relatively long, and the throttling opening is relatively small.

24. The scroll compressor capable of automatically adjusting back pressure according to claim 22, characterized in that: A second gap is provided between the outer peripheral wall of the second valve core (95) and the inner peripheral wall of the fifth channel (85) to form the throttling channel. When the gas pressure is relatively high, the length of the shaft section of the second valve core (95) entering the sixth channel (86) is relatively long, and the length of the shaft section located in the fifth channel (85) is relatively short. The length of the throttling through the second gap is relatively short, and the throttling opening is relatively large. When the gas pressure is relatively low, the length of the shaft section of the second valve core (95) entering the sixth channel (86) is relatively short, and the length of the shaft section located in the fifth channel (85) is relatively long. The length of the throttling through the second gap is relatively long, and the throttling opening is relatively small.

25. The scroll compressor capable of automatically adjusting back pressure according to claim 22, characterized in that: When the axial end of the second valve core (95) is not subjected to gas pressure, the second valve core (95) is entirely located in the fifth channel (85) or most of it is located in the fifth channel (85); when the axial end of the second valve core (95) is subjected to increased gas pressure, the length of the second valve core (95) entering the sixth channel (86) increases, resulting in a decrease in the throttling effect; when the axial end of the second valve core (95) is subjected to reduced gas pressure, the length of the second valve core (95) entering the sixth channel (86) decreases, resulting in an increase in the throttling effect.

26. The scroll compressor capable of automatically adjusting back pressure according to claim 22, characterized in that: The second elastic member (96) further comprises a second elastic member (96), one end of which is fixed to the first valve housing (94) and the other end of which is connected to the second valve core (95), and is capable of providing an elastic restoring force for the second valve core (95) to move in the direction of the fifth channel (85), and the other end of the second elastic member (96) is connected to the end of the second valve core (95) opposite to the axial end.

27. The scroll compressor capable of automatically adjusting back pressure according to claim 26, characterized in that: A second accommodating groove (97) is provided inside the second valve core (95), a portion of the second elastic member (96) is passed through the second accommodating groove (97), and the other end of the second elastic member (96) is fixedly connected to or abuts against the bottom of the second accommodating groove (97).

28. The scroll compressor capable of automatically adjusting back pressure according to claim 26, characterized in that: A second annular boss (951) extending radially outward is formed at the other axial end of the second valve core (95), and a second step (89) is formed at the junction of the fifth channel (85) and the sixth channel (86), and the second annular boss (951) can be matched and engaged with the second step (89) to form a limit; and / or, a second limit member (810) is provided at the end of the first valve housing (94) located downstream in the flow direction of the airflow, the second limit member (810) is fixedly connected to the first valve housing (94), one end of the second elastic member (96) is fixedly connected to the second limit member (810), and the second limit member (810) is also provided with a through hole for accommodating the passage of gas.

29. The scroll compressor capable of automatically adjusting back pressure according to any one of claims 22 to 28, characterized in that: An initial back pressure supply channel (12) is provided on the movable disc (1), one end of the initial back pressure supply channel (12) is communicated with the low pressure chamber or the medium pressure chamber in the compression chamber (11), and the other end is communicated with the back pressure chamber (5), so as to be able to release the pressure in the low pressure chamber or the medium pressure chamber into the back pressure chamber (5). The compression chamber (11) includes a low pressure chamber, a medium pressure chamber and a high pressure chamber, which are respectively a high pressure chamber, a medium pressure chamber and a low pressure chamber in descending order of pressure. The pressure of the high pressure chamber is equal to the pressure of the exhaust chamber (7).

30. The scroll compressor capable of automatically adjusting back pressure according to claim 29, characterized in that: A second one-way valve (13) is also provided in the initial back pressure supply channel (12), and the second one-way valve only allows the fluid to flow from the low pressure chamber or the medium pressure chamber to the back pressure chamber (5); and / or, a second throttle valve (14) is also provided in the initial back pressure supply channel (12), and the second throttle valve (14) is a columnar throttling spiral pin, and a spiral throttling groove is provided on its outer peripheral wall, and the second throttle valve (14) can achieve a fixed throttling effect on the fluid.

31. The scroll compressor capable of automatically adjusting back pressure according to claim 30, characterized in that: When both the second one-way valve (13) and the second throttle valve (14) are included, the second one-way valve (13) is also a one-way ball valve, and a fifth elastic member (15) is further provided in the initial back pressure supply channel (12), one end of the fifth elastic member (15) is connected to the second throttle valve (14), and the other end is connected to the second one-way valve (13).

32. The scroll compressor capable of automatically adjusting back pressure according to any one of claims 22 to 28, characterized in that: The second channel (82) includes a second channel 1 (821) and a second channel 2 (822), wherein the second channel 1 (821) extends along the axial direction of the bracket (3), and the central axis of the second channel 2 (822) forms an angle between 0° and 90° with the axis of the bracket (3), one end of the second channel 1 (821) is located at the axial end of the bracket (3) opposite to the cover body (4), and is connected to the first channel (81), the other end of the second channel 1 (821) is connected to one end of the second channel 2 (822), and the other end of the second channel 2 (822) extends to be connected to the back pressure chamber (5).

33. The scroll compressor capable of automatically adjusting back pressure according to claim 32, characterized in that: When the throttling pressure regulating device (9) comprises a first valve housing (94) and a second valve core (95), and the first valve housing (94) is located in the second channel (82), a notch (941) is provided on the first valve housing (94) at a position connected to the second channel 2 (822).

34. An air conditioner, characterized in that: The invention comprises the scroll compressor capable of automatically adjusting back pressure according to any one of claims 1 to 21, or the scroll compressor capable of automatically adjusting back pressure according to any one of claims 22 to 33.

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