Variable-capacity compressor and air conditioner

Abstract

The variable-capacity compressor comprises a first air cylinder, a second air cylinder and a partition plate, the second air cylinder is provided with a second sliding piece and a variable-capacity cavity, the partition plate is provided with a pressure relief opening, the pressure relief opening is communicated with the variable-capacity cavity, and the first air cylinder is provided with a valve groove and a pressure relief channel opposite to the pressure relief opening. The pressure relief channel is located between the valve groove and the pressure relief opening, at least part of the structure of the pressure relief valve is arranged in the valve groove, and the pressure relief valve can move in the valve groove and the pressure relief channel so that the pressure relief channel can be communicated with or disconnected from the pressure relief opening. The pressure relief valve comprises a first end and a second end which are opposite to each other, the first end is opposite to the pressure relief opening so as to bear the pressure of the pressure relief opening, the first air cylinder is further provided with a back pressure channel, and the back pressure channel can introduce fluid in the shell cavity so as to apply pressure to the second end. According to the invention, the problems of noise, jittering and the like generated when the variable-capacity compressor is started after long-time low-temperature standing can be solved.

Description

Technical Field

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

[0002] Scroll compressors have significant advantages such as small size and simple structure, and are widely used in residential air conditioners and multi-split air conditioning systems. In multi-split air conditioning applications, one outdoor unit connects to multiple indoor units simultaneously. When all indoor units are running, a large cooling capacity is required, and the outdoor unit operates at full load; when only one indoor unit is running, a small cooling capacity is required, and the outdoor unit operates at low load. Given the large load variations characteristic of multi-split air conditioning systems, inverter technology can meet the needs to some extent. However, when the indoor units are small, the compressor may still experience a cooling capacity surplus even when operating at its lower frequency limit. This leads to frequent compressor start-stop cycles, resulting in large fluctuations in indoor temperature and increased power consumption.

[0003] Based on the use of variable frequency technology in the rolling rotor compressor, a selectively operating variable displacement cylinder is installed on the pump body. When a small load is required, the variable displacement cylinder does not work; when a large load is required, the variable displacement cylinder works. This significantly reduces the minimum load of the unit and improves the problem of frequent start-stop when the unit is operating under relatively low load conditions, such as when only one indoor unit is running.

[0004] Under normal operating conditions, pressure pulsations within the variable-capacity refrigerant chamber of a residential multi-split air conditioning unit have no impact on operational stability. However, after the outdoor unit has been placed in low-temperature conditions for an extended period, the refrigerant inside the unit changes from a gaseous state to a liquid state. When the unit is turned on, a large amount of liquid refrigerant is drawn into the compressor and guided into the variable-capacity chamber through the variable-capacity port. Due to the incompressible nature of liquid refrigerant, the pressure within the variable-capacity chamber changes drastically with the reciprocating motion of the vanes, causing the compressor to vibrate violently and generate noise. This severely affects the safe operation of the unit and the comfort of its users.

[0005] Because existing variable capacity compressors have technical problems such as noise and vibration when starting up after being left to stand at low temperatures for a long time, this invention studies and designs a variable capacity compressor and an air conditioner. Summary of the Invention

[0006] Therefore, the present invention provides a variable capacity compressor and an air conditioner that can solve the technical problem that variable capacity compressors in the prior art are prone to noise and vibration when started after being left to stand at low temperature for a long time.

[0007] To address the above problems, the present invention provides a variable displacement compressor, comprising:

[0008] A first cylinder, a second cylinder, and a partition, wherein the partition is located between the first cylinder and the second cylinder;

[0009] The second cylinder is provided with a second sliding vane and a variable displacement cavity, and the tail end of the second sliding vane communicates with the variable displacement cavity.

[0010] The partition plate is provided with a pressure relief port, which communicates with the variable displacement cavity. The first cylinder is provided with a valve groove and a pressure relief channel opposite to the pressure relief port. The pressure relief channel is located between the valve groove and the pressure relief port. At least part of the structure of a pressure relief valve is provided in the valve groove. The pressure relief valve can move within the valve groove and the pressure relief channel to connect or disconnect the pressure relief port from the pressure relief channel, and can communicate with the compressor housing chamber through the pressure relief channel. The pressure relief valve includes a first end and a second end facing away from each other. The first end is opposite to the pressure relief port to withstand the pressure of the pressure relief port. The first cylinder is also provided with a back pressure channel, which can introduce fluid from the housing chamber to apply pressure to the second end.

[0011] In some implementations...

[0012] It also includes a crankshaft having a central axis. The pressure relief channel is disposed on the end face of the first cylinder facing the partition. The pressure relief channel extends radially along the first cylinder. In the projection plane of the longitudinal plane passing through the central axis, the radially inner end of the pressure relief channel is closer to the central axis of the crankshaft than the radially inner end of the valve groove. At the same time, the radially inner end of the pressure relief channel is closer to the central axis of the crankshaft than the radially inner end of the pressure relief port. The radially outer end of the pressure relief channel is farther away from the central axis of the crankshaft than the radially outer end of the partition.

[0013] In some implementations...

[0014] It also includes a crankshaft having a central axis, one end of the back pressure channel being connected to the valve groove, and the other end of the back pressure channel being connected to the axial side end face of the first cylinder through a back pressure groove, the axial side end face being the side end face away from the partition plate, and the back pressure groove being a recessed groove formed on the axial side end face of the first cylinder; and also includes a first flange, the first flange being connected to the axial side end face of the first cylinder, in the projection plane of the longitudinal plane passing through the central axis, the radially inner end of the back pressure groove being closer to the central axis of the crankshaft than the radially inner end of the back pressure channel, and the radially outer end of the back pressure groove being farther away from the central axis of the crankshaft than the radially outer end of the first flange, the radially outer end of the back pressure groove being connected to the housing chamber.

[0015] In some implementations...

[0016] The volume change V of the variable-volume cavity is determined by the thickness b of the second sliding vane, the axial height h of the second cylinder, and the crankshaft eccentricity e within the second cylinder, and its calculation formula is as follows: Where V is in units of The units of e, b and h are all mm, and the thickness of the second slide is the dimension of the second slide along the circumferential direction of the second cylinder.

[0017] The flow area S of the pressure relief port and the volume change V of the variable-volume cavity satisfy the following relationship: .

[0018] In some implementations...

[0019] .

[0020] In some implementations...

[0021] The pressure relief valve has a cylindrical structure, and the diameter D of the pressure relief valve, the lift L of the pressure relief valve, and the flow area S of the pressure relief port satisfy the following relationship: And / or L < 1.5 mm; where D and L are in mm, and S is in mm. 2 .

[0022] In some implementations...

[0023] The second cylinder is also provided with a variable displacement port and a connecting channel. The variable displacement port is opened from the radial outer end of the second cylinder toward the inside. The variable displacement port and the variable displacement cavity are located at different positions in the circumferential direction of the second cylinder. The variable displacement port and the variable displacement cavity are connected through the connecting channel. The variable displacement port can be connected to fluids of different pressures outside the variable displacement compressor, so that the pressure relief valve is connected to the partition to prevent pressure relief from the variable displacement cavity. At this time, the second sliding vane is not connected to the second roller, or the pressure relief valve is not connected to the partition to relieve pressure from the variable displacement cavity. At this time, the second sliding vane is connected to the second roller.

[0024] In some implementations...

[0025] When the pressure relief valve is connected to the partition, the pressure relief valve closes the connection between the pressure relief port and the pressure relief channel; when the pressure relief valve is not connected to the partition, the pressure relief valve opens the connection between the pressure relief port and the pressure relief channel, so that the variable displacement cavity releases fluid pressure into the compressor housing chamber through the pressure relief port and the pressure relief channel.

[0026] The first cylinder is located at the upper end of the partition plate, and the lower end of the pressure relief valve is the first end, so as to withstand the upward pressure F1 in the pressure relief port. The pressure in the pressure relief port is equal to the pressure in the variable volume chamber. The upper end of the pressure relief valve is the second end, which can withstand the downward pressure F2 applied to it in the back pressure channel. The pressure relief valve also withstands its own downward gravity G.

[0027] In some implementations...

[0028] When the force on the pressure relief valve is F1 < F2 + G, the pressure relief valve can move downward to connect with the partition, thereby closing the connection between the pressure relief port and the pressure relief channel; when the force on the pressure relief valve is F1 > F2 + G, the pressure relief valve can move upward to not connect with the partition, thereby opening the connection between the pressure relief port and the pressure relief channel, so that the variable volume cavity can release fluid pressure into the shell chamber through the pressure relief port and the pressure relief channel.

[0029] The present invention also provides an air conditioner comprising the aforementioned variable capacity compressor.

[0030] The variable capacity compressor and air conditioner provided by this invention have the following beneficial effects:

[0031] This invention provides a pressure relief port on a partition between the first and second cylinders, connecting it to a variable displacement chamber on the second cylinder (the variable displacement chamber is the chamber connected to the tail of the second slide plate, used to drive whether the second slide plate connects with the second roller to achieve variable displacement). Simultaneously, a valve groove and a pressure relief channel are provided on the first cylinder opposite the pressure relief port. A pressure relief valve is installed in the valve groove, with its first end facing the pressure relief port to withstand the pressure of the variable displacement chamber, and its second end facing the valve groove. The back pressure channel allows the pressure from the housing chamber to be introduced into the back pressure channel. In the valve groove, the second end of the pressure relief valve bears the pressure of the shell chamber. Therefore, the pressure relief valve will automatically move according to the pressure of the variable displacement cavity and the shell chamber at its two ends, respectively. In particular, it can open the connection between the pressure relief port and the pressure relief channel when the pressure in the variable displacement cavity is greater than the pressure in the shell chamber, realizing automatic pressure relief of the variable displacement cavity. It can automatically open the pressure relief valve when the pressure in the variable displacement cavity is high and automatically close the pressure relief valve when the pressure in the variable displacement cavity is low, solving the noise generated when the variable displacement compressor starts after a long period of low temperature and static storage. This invention addresses issues such as vibration; and compared to existing riveted exhaust valve plates, it offers improved reliability against abnormal liquid pressure, eliminating the repeated vibration of the free end of the thin-arm riveted valve plate under high-pressure airflow pulsation. This effectively improves stability during pressure relief, preventing noise or vibration caused by vibration, and provides faster response and superior timeliness of opening and closing. It effectively solves the technical problem of vibration caused by riveted exhaust valve plates in existing compressors. Furthermore, the pressure relief valve of this invention introduces pressure from within the housing at its second end. Compared to existing solutions that introduce pressure from within the cylinder, where the cylinder pressure is typically lower than the housing pressure, this would cause premature valve opening, leading to backflow of fluid within the housing and preventing effective pressure relief. Therefore, this invention achieves stable pressure relief, prevents vibration, provides faster response, and offers more precise pressure relief compared to various existing solutions. Moreover, this invention eliminates the need for additional piping for pressure relief, reducing compressor manufacturing costs and size. Attached Figure Description

[0032] To more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. The drawings described below are merely exemplary, and those skilled in the art can derive other embodiments based on the provided drawings without creative effort.

[0033] Figure 1 This is a longitudinal sectional view of the variable displacement compressor of the present invention at two air intake ports;

[0034] Figure 2 yes Figure 1 Top view of the second compression component;

[0035] Figure 3 yes Figure 2 A magnified image of BB;

[0036] Figure 4 This is a longitudinal sectional view of the variable displacement compressor of the present invention at the variable displacement port;

[0037] Figure 5 yes Figure 4 Top view of the first compression component;

[0038] Figure 6 yes Figure 5 AA enlarged view (pressure relief valve closed pressure relief port);

[0039] Figure 7 yes Figure 6 A magnified view of part C;

[0040] Figure 8 yes Figure 5 AA enlarged view (pressure relief valve open pressure relief port);

[0041] Figure 9 yes Figure 8 A magnified view of part D;

[0042] Figure 10 yes Figure 5 A bottom view of the structure of the first cylinder;

[0043] Figure 11 yes Figure 5 Top view of the first cylinder;

[0044] Figure 12 This is a graph showing the relationship between the pressure pulsation of the variable volume chamber and the S / V ratio of the present invention.

[0045] Figure 13 This is a graph showing the relationship between the wear of the diaphragm and the lift of the pressure relief valve in this invention.

[0046] The attached figures are labeled as follows:

[0047] 1. First cylinder; 2. Second cylinder; 3. Partition plate; 4. Second vane; 5. Variable volume chamber; 6. Pressure relief port; 7. Valve groove; 8. Pressure relief channel; 9. Shell chamber; 10. Pressure relief valve; 11. First end; 12. Second end; 13. Back pressure channel; 14. Back pressure groove; 15. First flange; 16. Variable volume port; 17. Connecting channel; 18. Second roller; 19. First intake port; 20. Second intake port; 21. Crankshaft; 22. First roller; 23. First vane; 24. Variable volume mechanism; 25. Elastic component; 26. Pin; 27. Shell; 28. Exhaust port; 29. ​​Second flange; 30. Distributor; 31. Variable volume component; 32. Electronic expansion valve; 33. Heat exchanger one; 34. Heat exchanger two; 35. Low-pressure valve; 36. High-pressure valve. Detailed Implementation

[0048] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. The following description of at least one exemplary embodiment is merely illustrative and is in no way intended to limit the present invention or its application or use. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0049] In the description of this invention, it should be understood that the orientation or positional relationship indicated by directional terms such as "front, back, up, down, left, right", "horizontal, vertical, horizontal" and "top, bottom" is generally based on the orientation or positional relationship shown in the accompanying drawings, and is only for the convenience of describing this invention and simplifying the description. Unless otherwise stated, these directional terms do not indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation on the scope of protection of this invention; the directional terms "inner" and "outer" refer to the inner and outer contours relative to the outline of each component itself.

[0050] For ease of description, spatial relative terms such as "above," "on top of," "on the upper surface of," "above," etc., are used herein to describe the spatial positional relationship of a device or feature as shown in the figures to other devices or features. It should be understood that spatial relative terms are intended to encompass different orientations in use or operation beyond the orientation of the device as described in the figures. For example, if the device in the figures were inverted, a device described as "above" or "on top of" other devices or structures would subsequently be positioned as "below" or "under" other devices or structures. Thus, the exemplary term "above" can include both "above" and "below." The device may also be positioned in other different ways, rotated 90 degrees, or in other orientations, and the spatial relative descriptions used herein will be interpreted accordingly.

[0051] Furthermore, it should be noted that the use of terms such as "first" and "second" to define components is merely for the purpose of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore should not be construed as limiting the scope of protection of this invention.

[0052] See also Figure 1-13 As shown, according to an embodiment of the present invention, a variable displacement compressor is provided, comprising:

[0053] A first cylinder 1, a second cylinder 2, and a partition 3, wherein the partition 3 is located between the first cylinder 1 and the second cylinder 2;

[0054] The second cylinder 2 is provided with a second sliding vane 4 and a variable displacement cavity 5, and the tail of the second sliding vane 4 is connected to the variable displacement cavity 5.

[0055] The partition 3 is provided with a pressure relief port 6, which is connected to the variable displacement cavity 5. The first cylinder 1 is provided with a valve groove 7 and a pressure relief channel 8 opposite to the pressure relief port 6. The pressure relief channel 8 is located between the valve groove 7 and the pressure relief port 6. At least part of the structure of the pressure relief valve 10 is provided in the valve groove 7. The pressure relief valve 10 can move in the valve groove 7 and the pressure relief channel 8 to connect or disconnect the pressure relief port 6 from the pressure relief channel 8, and can communicate with the housing chamber 9 of the compressor through the pressure relief channel 8. The pressure relief valve 10 includes a first end 11 and a second end 12 facing away from each other. The first end 11 is opposite to the pressure relief port 6 to withstand the pressure of the pressure relief port 6. The first cylinder 1 is also provided with a back pressure channel 13, which can introduce fluid in the housing chamber 9 to apply pressure to the second end 12.

[0056] This invention provides a pressure relief port on a partition between the first and second cylinders, connecting it to a variable displacement chamber on the second cylinder (the variable displacement chamber is the cavity connected to the tail of the second slide vane, used to drive whether the second slide vane connects with the second roller to achieve variable displacement). Simultaneously, a valve groove and a pressure relief channel are provided on the first cylinder opposite the pressure relief port. A pressure relief valve is installed in the valve groove, with its first end facing the pressure relief port to withstand the pressure of the variable displacement chamber, and its second end facing the valve groove. The back pressure channel allows fluid pressure from the housing chamber to be introduced into the back pressure channel. The pressure is introduced into the valve groove, causing the second end of the pressure relief valve to bear the pressure of the housing chamber. Therefore, the pressure relief valve automatically moves according to the pressure in the variable displacement cavity and the housing chamber at its two ends, respectively. Specifically, it opens the connection between the pressure relief port and the pressure relief channel when the pressure in the variable displacement cavity is greater than the pressure in the housing chamber, achieving automatic pressure relief of the variable displacement cavity. This allows the pressure relief valve to automatically open when the pressure in the variable displacement cavity is high and automatically close when the pressure in the variable displacement cavity is low, thus solving the noise problem generated when starting a variable displacement compressor after a long period of low-temperature quiescence. This invention addresses issues such as vibration and tremors. Compared to existing riveted exhaust valve plates, this invention offers improved reliability against abnormal liquid pressure, preventing the free end of the thin-arm riveted valve plate from repeatedly vibrating under high-pressure airflow pulsation. It effectively improves stability during pressure relief, preventing noise or vibration caused by vibration, and offers faster response and superior timeliness in opening and closing. It effectively solves the technical problem of vibration caused by riveted exhaust valve plates in existing compressors. Furthermore, the pressure relief valve of this invention introduces pressure from within the housing at its second end. Compared to existing solutions that introduce pressure from within the cylinder, where the cylinder pressure is typically lower than the housing pressure, this would cause premature valve opening, leading to backflow of fluid within the housing and preventing effective pressure relief. Therefore, this invention achieves stable pressure relief, prevents vibration, offers faster response, and provides more precise pressure relief compared to various existing solutions. Moreover, this invention eliminates the need for additional piping for pressure relief, reducing compressor manufacturing costs and size.

[0057] This invention also solves the following technical problems:

[0058] 1. It solves the problems of noise and vibration generated when starting up a variable capacity compressor after a long period of low-temperature static storage; it also solves the technical problem that the use of riveted exhaust valve plates in existing compressors can cause vibration.

[0059] 2. Avoid introducing pressure into the cylinder body as back pressure, which could cause fluid backflow in the housing and prevent normal pressure relief.

[0060] 3. When conventional two-stage (enthalpy-increasing) compressors and systems using them are left stagnant for a long time in low-temperature environments (especially ultra-low temperature environments below -20℃), or when the system load changes significantly or the evaporator heat exchange is poor, liquid slugging can cause a sudden increase in the pressure of the intermediate-pressure chamber, which in turn can lead to overpressure tripping of the secondary compression chamber, affecting the stable operation of the system.

[0061] 4. Existing pressure relief technology solutions that involve setting external pipelines and differential pressure control valves require additional system pipelines and control valves, which increases manufacturing costs and makes the pipeline layout more complex, thus affecting the overall heating performance and system reliability.

[0062] In some implementations...

[0063] It also includes a crankshaft 21, which has a central axis. The pressure relief channel 8 is disposed on the end face of the first cylinder 1 facing the partition 3. The pressure relief channel 8 extends in the radial direction of the first cylinder 1. In the projection plane of the longitudinal plane passing through the central axis, the radial inner end of the pressure relief channel 8 is closer to the central axis of the crankshaft 21 than the radial inner end of the valve groove 7. At the same time, the radial inner end of the pressure relief channel 8 is closer to the central axis of the crankshaft 21 than the radial inner end of the pressure relief port 6. The radial outer end of the pressure relief channel 8 is farther away from the central axis of the crankshaft 21 than the radial outer end of the partition 3.

[0064] This is a preferred structural form of the pressure relief channel of the present invention, namely, a channel provided on the end face of the first cylinder facing the partition and extending radially. Moreover, the radial inner end of the pressure relief channel extends beyond the inner end of the valve groove and the radial inner end of the pressure relief port, which can increase the length of the pressure relief channel and increase the length of the pressure relief channel as a venting channel to vent air to the second end of the pressure relief valve, thereby improving the pressure relief effect and the venting performance. The radial outer end of the pressure relief channel extends to the radial outer end of the partition, which can enhance its communication with the inner cavity of the housing, effectively venting the fluid in the variable volume cavity to the inner cavity of the housing.

[0065] In some implementations...

[0066] It also includes a crankshaft 21, which has a central axis. One end of the back pressure channel 13 is connected to the valve groove 7, and the other end of the back pressure channel 13 is connected to the axial side end face of the first cylinder 1 through a back pressure groove 14. The axial side end face is the side end face away from the partition 3. The back pressure groove 14 is a recessed groove formed on the axial side end face of the first cylinder 1. It also includes a first flange 15, which is connected to the axial side end face of the first cylinder 1. In the projection plane of the longitudinal plane passing through the central axis, the radial inner end of the back pressure groove 14 is closer to the central axis of the crankshaft 21 than the radial inner end of the back pressure channel 13, and the radial outer end of the back pressure groove 14 is farther away from the central axis of the crankshaft 21 than the radial outer end of the first flange 15. The radial outer end of the back pressure groove 14 is connected to the housing chamber 9.

[0067] This is a preferred structural form of the back pressure channel on the first cylinder of the present invention. By providing a back pressure groove structure on the axial end face of the first cylinder facing the first flange, and having its radial outer end extend beyond the radial outer end of the first flange, fluid (exhaust fluid) can be effectively introduced from the inner cavity of the housing into the back pressure channel, thereby acting on the second end of the pressure relief valve. This achieves the purpose of the pressure relief valve automatically opening and closing the pressure relief channel according to the pressure of the variable volume chamber and the pressure of the inner cavity of the housing. Furthermore, the radial inner end of the back pressure groove extends beyond the radial inner end of the back pressure channel, which can increase the connection distance and connection length between the back pressure groove and the back pressure channel, enhance the back pressure introduction effect, and improve the purpose of automatic pressure relief.

[0068] In some implementations...

[0069] The volume change V of the variable-volume cavity 5 is determined by the thickness b of the second sliding vane 4, the axial height h of the second cylinder 2, and the crankshaft eccentricity e within the second cylinder 2, and its calculation formula is as follows: Where V is in units of The units of e, b and h are all mm. The thickness of the second slide 4 is the dimension of the second slide 4 along the circumferential direction of the second cylinder 2.

[0070] The flow area S of the pressure relief port 6 and the volume change V of the variable volume cavity 5 satisfy the following relationship: .

[0071] The larger the change in volume of the variable-volume cavity in this invention, the larger the required flow area S of the pressure relief port must be. This ensures that the fluid in the variable-volume cavity is discharged into the casing as quickly as possible, suppressing the pressure rise caused by the accumulation of a large amount of liquid refrigerant in the variable-volume cavity during low-temperature static startup of the compressor. Experiments have verified that the flow area S of the pressure relief port and the change in volume V of the variable-volume cavity satisfy the following relationship: At this time, it can suppress the sharp increase in pressure pulsation in the compression chamber, and at this time the pressure pulsation in the variable displacement chamber is reduced to 1MPa, such as Figure 12 As shown. When At this time, the pressure pulsation in the variable displacement cavity can be reduced to 0.2MPa, which greatly reduces the pressure pulsation in the variable displacement cavity when the compressor is started at low temperature and stationary.

[0072] In some implementations...

[0073] .

[0074] In some implementations...

[0075] The pressure relief valve 10 has a cylindrical structure, and the diameter D of the pressure relief valve 10 (i.e., Figure 9 The φD in the figure, the lift L of the pressure relief valve 10 and the flow area S of the pressure relief port 6 satisfy the following relationship: ; and / or L < 1.5 mm; where D and L are in mm, and S is in mm. 2 .

[0076] The diameter D and lift L of the pressure relief valve in this invention affect the velocity at which the refrigerant in the variable volume cavity is discharged into the housing through the pressure relief port and pressure relief channel. Therefore, the flow area through the pressure relief valve must be larger than the flow area of ​​the pressure relief port, i.e. This invention ensures that the pressure relief valve can completely and effectively close the pressure relief port. When the pressure relief valve reciprocates within the valve slot of the first cylinder, it repeatedly strikes the intermediate partition adjacent to the first cylinder 1. If the pressure relief valve lift L is too large, it can easily damage the intermediate partition, reducing the reliability of the compressor. Therefore, it is necessary to strictly control the pressure relief valve lift. After repeated verification, when L meets the condition: L < 1.5 mm, the wear on the intermediate partition caused by the pressure relief valve striking the partition can be significantly reduced. Figure 13 As shown.

[0077] In some implementations...

[0078] The second cylinder 2 is also provided with a variable displacement port 16 and a connecting channel 17. The variable displacement port 16 is opened from the radial outer end of the second cylinder 2 toward the inside. The variable displacement port 16 and the variable displacement cavity 5 are located at different circumferential positions of the second cylinder 2. The variable displacement port 16 and the variable displacement cavity 5 are connected through the connecting channel 17. The variable displacement port 16 can be connected to fluids of different pressures outside the variable displacement compressor, so that the pressure relief valve 10 is connected to the partition 3 to prevent pressure relief from the variable displacement cavity 5. At this time, the second sliding vane 4 is not connected to the second roller 18, or the pressure relief valve 10 is not connected to the partition 3 to relieve pressure from the variable displacement cavity 5. At this time, the second sliding vane 4 is connected to the second roller 18.

[0079] This is a further preferred structural form of the second cylinder of the present invention. Through the variable displacement port and the connecting channel, fluid can be introduced from outside the compressor and enter the variable displacement chamber. The pressure relief valve is automatically opened or closed according to the relationship between the pressure and the pressure in the housing. The second sliding vane is automatically driven to engage with the second roller according to the relationship between the pressure and the pressure in the compression chamber, so as to realize the variable displacement operation of compression or non-compression. While realizing variable displacement control, it can also effectively relieve pressure in the variable displacement chamber, preventing noise, vibration and other issues that may occur when the compressor is started after being left to stand at low temperature for a long time.

[0080] The present invention relates to a compressor structure: This invention relates to a rolling rotor compressor, comprising a distributor 30, a housing 27, a motor, and a pump body. The distributor 30 is disposed outside the housing 27, the motor is sleeved on the upper part of the housing 27, and the pump body is sleeved inside the housing 27 and located below the motor. The pump body includes a first flange 15, a second flange 29, a first compression section, a second compression section, a partition plate (partition plate 3), and a crankshaft 21. The crankshaft 21 is sequentially sleeved on the motor rotor, the first flange 15, the first roller 22, the partition plate 3, the second roller 18, and the second flange 29. The first compression section includes a first cylinder 1, a first roller 22, and a first vane 23. The first roller 22 is sleeved on the crankshaft 21 and located inside the first cylinder 1. The first vane 23 is disposed in a vane groove of the first cylinder 1, one end of which abuts against the outer circle of the first roller 22, dividing the first cylinder 1 into an intake chamber and a compression chamber, and the other end communicates with the high pressure inside the housing. The second compression section includes a second cylinder 2, a second roller 18, and a second vane 4. The second roller 18 is sleeved on the crankshaft and located inside the second cylinder 2. The second vane 4 is disposed in the vane groove of the second cylinder 2, with one end abutting against the outer circle of the second roller 18, dividing the first cylinder 1 into an intake chamber and a compression chamber. The other end is surrounded by a partition plate, a second flange 29, and the second cylinder 2 to form a variable-volume chamber isolated from the high pressure inside the housing. The partition plate is located between the first and second compression sections. The refrigerant passes through the liquid separator intake port, the first intake port 19, and the second intake port 20 through the housing and communicates with the intake ports of the first cylinder 1 and the second cylinder 2 respectively (the two cylinders are preferably connected in parallel).

[0081] When high-pressure refrigerant is introduced into the variable-capacity cavity through the variable-capacity port, the second vane 4 abuts against the second roller 18. Driven by the motor rotor, the crankshaft simultaneously drives the first roller 22 and the second roller 18 to rotate. The first and second compression sections respectively draw in refrigerant, compress it, and discharge it into the housing and out through the exhaust pipe.

[0082] When low-pressure refrigerant is introduced into the variable-capacity cavity through the variable-capacity port, the second vane 4 is pushed into the vane slot of the second cylinder 2 by the second roller 18. Driven by the motor rotor, the crankshaft simultaneously drives the first roller and the second roller 18 to rotate. The first compression section draws in refrigerant, compresses it, and discharges it into the housing and out through the exhaust pipe. In the second compression section, the vane and roller are separated, and the process of drawing in refrigerant and compressing it cannot take place; at this time, the second compression section does not work.

[0083] The operating principle of the pressure relief valve of the present invention is as follows: When low-pressure refrigerant is introduced into the variable-capacity cavity 5 on the second compression section through the variable-capacity port 16, the second slide 4 is pushed into the slide groove of the second cylinder 2. The pressure on the side of the pressure relief valve located at the pressure relief port is less than the pressure on the side of the pressure relief valve located at the back pressure channel. The pressure relief valve moves to the side of the pressure relief port and closes the pressure relief port. The variable-capacity cavity maintains a low-pressure state, and the second compression section enters a non-working state.

[0084] When high-pressure refrigerant is introduced into the variable-volume cavity of the second compression section through the variable-volume port 16, the second sliding vane 4 moves towards and abuts against the second roller under the high pressure inside the variable-volume cavity, and the second compression section enters the working state. During the movement of the second sliding vane, the pressure inside the variable-volume cavity fluctuates according to a sine or cosine pattern, sometimes higher than the pressure inside the housing 27, and sometimes lower. When the pressure on the side of the pressure relief valve 10 located at the pressure relief port is less than the pressure on the side of the pressure relief valve located in the back pressure channel, the pressure relief valve moves towards the pressure relief port, closing the pressure relief port; when the pressure on the side of the pressure relief valve located at the pressure relief port is greater than the pressure on the side of the pressure relief valve located in the back pressure channel, the pressure relief valve moves towards the back pressure channel, opening the pressure relief port, and the fluid in the variable-volume cavity is discharged into the housing through the pressure relief channel, suppressing the pressure rise inside the variable-volume cavity.

[0085] This invention can achieve variable capacity control while also effectively relieving pressure in the variable capacity cavity, preventing noise and vibration from occurring when the compressor is started after being left to stand at low temperature for a long time.

[0086] In some implementations...

[0087] When the pressure relief valve 10 is connected to the partition 3, the pressure relief valve 10 closes the connection between the pressure relief port 6 and the pressure relief channel 8; when the pressure relief valve 10 is not connected to the partition 3, the pressure relief valve 10 opens the connection between the pressure relief port 6 and the pressure relief channel 8, so that the variable displacement cavity 5 releases fluid pressure to the compressor housing chamber 9 through the pressure relief port 6 and the pressure relief channel 8;

[0088] The first cylinder 1 is located at the upper end of the partition 3. The lower end of the pressure relief valve 10, i.e. the first end 11, is to withstand the upward pressure F1 from the pressure relief port 6. The pressure in the pressure relief port 6 is equal to the pressure in the variable volume chamber 5. The upper end of the pressure relief valve 10, i.e. the second end 12, can withstand the downward pressure F2 applied to it from the back pressure channel 13. The pressure relief valve 10 also withstands its own downward gravity G.

[0089] This is the preferred relationship between the movement state of the pressure relief valve of the present invention and whether or not there is a connection between the first and the pressure relief channel. That is, when the pressure relief valve moves to the point of contact with the partition, the connection between the pressure relief port and the pressure relief channel is effectively closed, and no pressure is released at this time. When the pressure relief valve moves to the point of not contacting the partition, the connection between the pressure relief port and the pressure relief channel is effectively opened, and the fluid in the variable volume chamber is released to the shell chamber through the pressure relief port and the pressure relief channel.

[0090] The pressure relief valve of the present invention automatically opens or closes the connection between the pressure relief port and the pressure relief channel according to the magnitude of the pressure at both ends and the magnitude of gravity. The automatic pressure relief process is that the upper end of the pressure relief valve bears the pressure of the back pressure channel, i.e., the inner cavity of the housing, and the lower end of the pressure relief valve bears the pressure of the pressure relief port, i.e., the variable volume cavity. The gravity of the pressure relief valve of the present invention is G. Since its gravity is relatively small compared with the pressure above and below, it can be ignored. Therefore, it can automatically open the pressure relief channel to relieve pressure in the variable volume cavity or close the pressure relief according to the pressure relationship between the variable volume cavity and the inner cavity of the housing.

[0091] In some implementations...

[0092] When the force on the pressure relief valve 10 is F1 < F2 + G, the pressure relief valve 10 can move downward to connect with the partition 3, thereby closing the connection between the pressure relief port 6 and the pressure relief channel 8; when the force on the pressure relief valve 10 is F1 > F2 + G, the pressure relief valve 10 can move upward to not connect with the partition 3, thereby opening the connection between the pressure relief port 6 and the pressure relief channel 8, so that the variable volume cavity 5 releases fluid pressure into the shell chamber 9 through the pressure relief port 6 and the pressure relief channel 8.

[0093] This invention's pressure relief valve further utilizes the magnitude of the pressure at both ends and the magnitude of gravity to automatically open or close the connection between the pressure relief port and the pressure relief channel. The automatic pressure relief process involves the upper end of the pressure relief valve bearing the pressure of the back pressure channel (i.e., the inner cavity of the housing), and the lower end bearing the pressure of the pressure relief port (i.e., the variable volume cavity). The weight of the pressure relief valve in this invention is G. Since its weight is relatively small compared to the fluid pressure above and below, it can be ignored. Preferably, when F1 < F2 + G, the pressure in the variable volume cavity is not very large. At this time, the pressure relief valve connects to the partition assembly to close the connection between the pressure relief port and the pressure relief channel, and no pressure is released. Preferably, when F1 > F2 + G, the pressure in the variable volume cavity is larger. At this time, the pressure relief valve is automatically pushed upward to open the connection between the pressure relief port and the pressure relief channel, achieving automatic pressure relief. Therefore, it can automatically open the pressure relief channel to relieve pressure in the variable volume cavity or close the pressure relief based on the pressure relationship between the variable volume cavity and the inner cavity of the housing.

[0094] The present invention also provides an air conditioner comprising the aforementioned variable capacity compressor.

[0095] The beneficial effects of this invention are:

[0096] This invention proposes an innovative two-stage compressor structure, which achieves the following beneficial effects by setting a pressure relief structure in the intermediate pressure chamber:

[0097] 1. This invention overcomes the noise and vibration issues that occur when a variable capacity compressor is started after being left to stand at low temperatures for a long time; and it can also avoid vibrations caused by flutter during the pressure relief process, thus achieving stable pressure relief.

[0098] 2. This invention also avoids introducing cylinder pressure as back pressure, which would cause fluid in the housing to flow back into the variable volume chamber, thus ensuring the accuracy of pressure relief and achieving stable pressure relief;

[0099] 3. To achieve dynamic pressure relief between the intermediate chamber pressure and the shell pressure, when the two-stage (enthalpy-increasing) compressor and the system using it are left stagnant in a low-temperature environment for a long time, or when the system load changes significantly or the evaporator heat exchange is poor, the pressure in the intermediate chamber may rise suddenly due to liquid slugging. This can relieve pressure in time to avoid overpressure tripping of the secondary compression chamber, thereby achieving precise tripping protection for the compressor and system and ensuring stable system operation.

[0100] 4. The present invention has a simple structure and is easy to implement. It does not require additional piping and control valve components, and the system piping layout does not need to be changed. The manufacturing cost is low. At the same time, changes to the wall system piping layout will not affect the overall heating performance and system reliability. It reduces the manufacturing cost of the compressor and avoids the impact on the overall heating performance and system reliability due to the complexity of the piping layout.

[0101] It will be readily understood by those skilled in the art that, without conflict, the advantageous technical features and embodiments of the above-described methods can be freely combined and superimposed.

[0102] The above description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A variable displacement compressor, characterized in that: include: A first cylinder (1), a second cylinder (2), and a partition (3), wherein the partition (3) is located between the first cylinder (1) and the second cylinder (2); The second cylinder (2) is provided with a second sliding vane (4) and a variable displacement cavity (5), and the tail of the second sliding vane (4) is connected to the variable displacement cavity (5). The partition (3) is provided with a pressure relief port (6), which is connected to the variable displacement cavity (5). The first cylinder (1) is provided with a valve groove (7) and a pressure relief channel (8) opposite to the pressure relief port (6). The pressure relief channel (8) is located between the valve groove (7) and the pressure relief port (6). At least part of the structure of a pressure relief valve (10) is provided in the valve groove (7). The pressure relief valve (10) can move in the valve groove (7) and the pressure relief channel (8) to make the pressure relief port (6)... The pressure relief valve (10) is connected to or disconnected from the pressure relief channel (8) and can be connected to the housing chamber (9) of the compressor through the pressure relief channel (8); the pressure relief valve (10) includes a first end (11) and a second end (12) facing each other. The first end (11) is opposite to the pressure relief port (6) to withstand the pressure of the pressure relief port (6). The first cylinder (1) is also provided with a back pressure channel (13), which can introduce fluid in the housing chamber (9) to apply pressure to the second end (12).

2. The variable displacement compressor according to claim 1, characterized in that: It also includes a crankshaft (21) having a central axis. The pressure relief channel (8) is disposed on the end face of the first cylinder (1) facing the partition (3). The pressure relief channel (8) extends in the radial direction of the first cylinder (1). In the projection plane of the longitudinal plane passing through the central axis, the radial inner end of the pressure relief channel (8) is closer to the central axis of the crankshaft (21) than the radial inner end of the valve groove (7). At the same time, the radial inner end of the pressure relief channel (8) is closer to the central axis of the crankshaft (21) than the radial inner end of the pressure relief port (6). The radial outer end of the pressure relief channel (8) is farther away from the central axis of the crankshaft (21) than the radial outer end of the partition (3).

3. The variable displacement compressor according to claim 1, characterized in that: It also includes a crankshaft (21) having a central axis, one end of the back pressure channel (13) being connected to the valve groove (7), and the other end of the back pressure channel (13) being connected to the axial side end face of the first cylinder (1) via a back pressure groove (14), the axial side end face being the side end face away from the partition plate (3), and the back pressure groove (14) being a recessed groove formed on the axial side end face of the first cylinder (1); and also includes a first flange (15), the first flange ( 15) It is connected to the axial side end face of the first cylinder (1). In the projection plane of the longitudinal plane passing through the central axis, the radial inner end of the back pressure groove (14) is closer to the central axis of the crankshaft (21) than the radial inner end of the back pressure channel (13). The radial outer end of the back pressure groove (14) is farther away from the central axis of the crankshaft (21) than the radial outer end of the first flange (15). The radial outer end of the back pressure groove (14) is connected to the housing chamber (9).

4. The variable displacement compressor according to claim 1, characterized in that: The volume change V of the variable-volume cavity (5) is determined by the thickness b of the second sliding vane (4), the axial height h of the second cylinder (2), and the crankshaft eccentricity e within the second cylinder (2), and its calculation formula is as follows: Where V is in units of The units of e, b and h are all mm. The thickness of the second slide (4) is the dimension of the second slide (4) along the circumferential direction of the second cylinder (2). The flow area S of the pressure relief port (6) and the volume change V of the variable volume cavity (5) satisfy the following relationship: .

5. The variable displacement compressor according to claim 4, characterized in that: 。 6. The variable displacement compressor according to claim 1, characterized in that: The pressure relief valve (10) has a cylindrical structure. The diameter D of the pressure relief valve (10), the lift L of the pressure relief valve (10), and the flow area S of the pressure relief port (6) satisfy the following relationship: And / or L < 1.5 mm; where D and L are in mm, and S is in mm. 2 .

7. The variable displacement compressor according to claim 1, characterized in that: The second cylinder (2) is also provided with a variable displacement port (16) and a connecting channel (17). The variable displacement port (16) is opened from the radial outer end of the second cylinder (2) toward the inside. The variable displacement port (16) and the variable displacement cavity (5) are located at different circumferential positions on the second cylinder (2). The variable displacement port (16) and the variable displacement cavity (5) are connected through the connecting channel (17). The variable displacement port (16) can be connected to fluids of different pressures outside the variable displacement compressor so that the pressure relief valve (10) is connected to the partition (3) to prevent pressure relief from the variable displacement cavity (5). At this time, the second sliding vane (4) is not connected to the second roller (18), or the pressure relief valve (10) is not connected to the partition (3) to relieve pressure from the variable displacement cavity (5). At this time, the second sliding vane (4) is connected to the second roller (18).

8. The variable displacement compressor according to claim 7, characterized in that: When the pressure relief valve (10) is connected to the partition (3), the pressure relief valve (10) closes the connection between the pressure relief port (6) and the pressure relief channel (8); when the pressure relief valve (10) is not connected to the partition (3), the pressure relief valve (10) opens the connection between the pressure relief port (6) and the pressure relief channel (8), so that the variable displacement cavity (5) releases fluid pressure to the compressor housing chamber (9) through the pressure relief port (6) and the pressure relief channel (8); The first cylinder (1) is located at the upper end of the partition (3), and the lower end of the pressure relief valve (10) is the first end (11) to withstand the upward pressure F1 in the pressure relief port (6). The pressure in the pressure relief port (6) is equal to the pressure in the variable volume chamber (5). The upper end of the pressure relief valve (10) is the second end (12). The second end (12) can withstand the downward pressure F2 applied to it in the back pressure channel (13). The pressure relief valve (10) also withstands its own downward gravity G.

9. The variable displacement compressor according to claim 8, characterized in that: When the force on the pressure relief valve (10) is F1 < F2 + G, the pressure relief valve (10) can move downward to connect with the partition (3), and close the connection between the pressure relief port (6) and the pressure relief channel (8) through the pressure relief valve (10); when the force on the pressure relief valve (10) is F1 > F2 + G, the pressure relief valve (10) can move upward to not connect with the partition (3), and open the connection between the pressure relief port (6) and the pressure relief channel (8) through the pressure relief valve (10), so that the variable volume cavity (5) releases fluid into the shell chamber (9) through the pressure relief port (6) and the pressure relief channel (8).

10. An air conditioner, characterized in that, The variable displacement compressor includes any one of claims 1-9.

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