Multi-stage variable-capacity compressor and air conditioning system

Abstract

The invention discloses a multi-stage variable-capacity compressor and an air conditioning system, belongs to the technical field of compressors, and aims to solve the problems that the axial space of an air cylinder of an existing variable-capacity compressor is limited, and the rigidity of the air cylinder is weakened, the multi-stage variable-capacity compressor comprises the air cylinder and a cylinder cover covering the end face of the air cylinder, and the air cylinder is provided with an air suction hole; the multi-stage variable-capacity compressor further comprises a middle plate, an arc-shaped movement assembly and a resistance assembly, the middle plate is arranged between the air cylinder and the cylinder cover and provided with a plurality of bypass holes distributed in the circumferential direction in a penetrating mode, an annular movement channel is formed in the side, facing the middle plate, of the cylinder cover, and the arc-shaped movement assembly is in clearance fit in the annular movement channel. The resistance assembly applies reset resistance to the arc-shaped movement assembly, suction pressure and exhaust pressure are introduced into the two ends of the annular movement channel respectively, and the arc-shaped movement assembly slides in the circumferential direction of the annular movement channel under the action of the pressure difference and the resistance assembly, so that flow paths between the bypass holes and the suction holes are blocked or communicated, and self-adaptive displacement adjustment is achieved.

Description

A multi-stage variable capacity compressor and air conditioning system Technical Field

[0001] This invention relates to the field of compressor technology, specifically to a multi-stage variable capacity compressor capable of automatically adjusting displacement according to operating conditions and an air conditioning system using the compressor. Background Technology

[0002] In variable frequency air conditioning systems, rotary compressors experience reduced motor efficiency and increased speed fluctuations when operating at low speeds. To address this, existing technologies typically employ variable capacity technology, which reduces the compressor's displacement under low load conditions to increase its speed, allowing the compressor motor to operate within a higher speed range.

[0003] In related technologies, to achieve multi-stage variable displacement, mounting holes are typically machined in the sidewall of the cylinder or inside the flange, and a valve core that moves along the cylinder axis is installed to control the opening and closing of bypass holes distributed at different axial positions. However, this structure has limitations in practical applications: on the one hand, the number of bypass holes arranged axially is limited by the axial height of the cylinder, resulting in fewer stages of variable displacement adjustment in the compressor; on the other hand, directly machining mounting holes and flow channels on the cylinder body or flange weakens the structural rigidity of the cylinder assembly, making the cylinder prone to deformation under high-pressure conditions, changing the fit clearance of moving parts and causing refrigerant leakage, thus reducing the reliability of the compressor.

[0004] Therefore, providing a multi-stage variable displacement compressor that avoids weakening the rigidity of the cylinder assembly and can increase the number of variable displacement adjustment stages is a technical problem that urgently needs to be solved in this field.

[0005] It should be noted that the information disclosed in the background section above is only used to enhance the understanding of the background of the present invention, and therefore may include information that does not constitute prior art known to those skilled in the art. Summary of the Invention

[0006] To address the problems in the prior art, the present invention aims to provide a multi-stage variable capacity compressor and air conditioning system, which solves the technical problems of existing variable capacity compressors, such as weakened structural rigidity due to the installation holes inside the cylinder or flange body, and limited number of bypass holes and variable capacity adjustment stages due to the limitation of cylinder axial height.

[0007] This invention provides a multi-stage variable displacement compressor, including a cylinder and a cylinder head covering the cylinder end face. The cylinder has an intake port. It also includes an adaptive variable displacement mechanism, comprising: an intermediate plate disposed between the cylinder and the cylinder head, with multiple bypass holes circumferentially distributed through the intermediate plate; an annular motion channel formed on the side of the cylinder head facing the intermediate plate, with one end of each bypass hole located within the cylinder cavity and the other end projecting into the annular motion channel; an arc-shaped motion component, clearance-fitted within the annular motion channel, capable of shielding a portion of the annular motion channel; and a resistance assembly. The component, located within the annular motion channel and acting on the arc-shaped motion assembly, applies a reset resistance to the arc-shaped motion assembly. One end of the annular motion channel introduces the compressor's suction pressure through a return channel, and the other end introduces the compressor's discharge pressure through a pressure-inducing channel. The arc-shaped motion assembly is configured to withstand the discharge pressure and suction pressure at both ends respectively. It is located between the discharge pressure and the suction pressure and slides circumferentially along the annular motion channel under the pressure difference between the discharge pressure and the suction pressure and the action of the resistance component, thereby blocking or connecting the flow path between one or more of the multiple bypass holes and the suction hole.

[0008] In some alternative embodiments, the arc-shaped motion assembly includes an arc-shaped slider and an arc-shaped slip ring that are interconnected or integrally formed; one end of the arc-shaped slider is connected to the resistance assembly and bears the intake pressure, while the other end bears the exhaust pressure; the arc-shaped slip ring is a non-closed arc-shaped structure with a notch formed in the circumferential direction, and the arc-shaped slip ring moves synchronously with the arc-shaped slider to fit against the lower surface of the intermediate plate to cover the annular motion channel, and one or more bypass holes can be exposed to the annular motion channel through the notch of the arc-shaped slip ring.

[0009] In some optional embodiments, the annular motion channel has a first circumferential section and a second circumferential section. The first circumferential section is an arc-shaped motion groove with a return hole at one end for connecting to the return channel and a pressure-inducing hole at the other end for connecting to the pressure-inducing channel. The second circumferential section is a cut-off section located between the return hole and the pressure-inducing hole to isolate the return hole and the pressure-inducing hole.

[0010] In some optional embodiments, a thrust-stop structure is provided on the side of the motion slot near the pressure-inlet hole. The thrust-stop structure is configured to limit the extreme position of the arc-shaped motion component when the resistance component pushes the arc-shaped motion component to reset, so that an intake gap for establishing supply and exhaust pressure is maintained between the arc-shaped motion component and the pressure-inlet hole.

[0011] In some alternative embodiments, the thrust structure is configured as a limiting step protruding into the annular movement channel.

[0012] In some optional embodiments, with the center of the cylinder's vane groove as the 0° reference, the distribution angle range α of the multiple bypass holes satisfies: 60° < α < 210°.

[0013] In some optional embodiments, the refrigerant compressed by the cylinder is discharged into the inner cavity of the housing of the multi-stage variable capacity compressor. The pressure inlet is open through the cylinder head and connects to the inner cavity of the housing of the multi-stage variable capacity compressor; the return outlet is connected to the intake outlet.

[0014] In some alternative embodiments, the cylinder contains an annular piston, and multiple bypass holes are located in the region between the movement trajectory of the outer ring of the piston within the cylinder and the movement trajectory of the inner ring of the piston within the cylinder.

[0015] In some alternative embodiments, the resistance component is selected from one or a combination of helical springs, rubber elastic elements, magnetic repulsion components, or shape memory alloy components.

[0016] This invention also provides an air conditioning system, including the multi-stage variable capacity compressor described above.

[0017] The multi-stage variable-capacity compressor and air conditioning system provided by this invention have the following advantages: This invention utilizes the suction and discharge pressure difference to drive the automatic adjustment of the compressor displacement according to changes in operating load. This allows the compressor to increase its operating speed by reducing displacement under low-load conditions, thereby improving motor efficiency and reducing vibration. Furthermore, this adaptive adjustment process requires no external electronic control components. Simultaneously, this invention avoids machining flow channels or mounting holes inside the cylinder body to accommodate the variable-capacity mechanism, maintaining the structural rigidity of the cylinder assembly and reducing the risk of cylinder deformation and refrigerant leakage under high-pressure conditions. In addition, this invention breaks through the physical space limitations imposed by the axial height of the cylinder on the variable-capacity components in traditional structures. By adopting a circumferential spatial layout, it increases the number of stages of variable-capacity adjustment, improving the compressor's adaptability to different load conditions. Attached Figure Description

[0018] Other features, objects, and advantages of the invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings.

[0019] Figure 1 is a three-dimensional structural diagram of a cylinder assembly in a multi-stage variable displacement compressor provided in an embodiment of the present invention; Figure 2 is a structural diagram of an intermediate plate provided in an embodiment of the present invention; Figure 3 is a structural diagram of an arc-shaped motion assembly provided in an embodiment of the present invention; Figure 4 is a schematic diagram of the cooperation relationship of the adaptive variable displacement mechanism in the variable displacement closed state provided in an embodiment of the present invention; Figure 5 is a schematic diagram of the bypass hole state of the intermediate plate in the variable displacement closed state of the adaptive variable displacement mechanism provided in an embodiment of the present invention; Figure 6 is a schematic diagram of the cooperation relationship of the adaptive variable displacement mechanism in the first variable displacement state provided in an embodiment of the present invention; Figure 7 is a schematic diagram of the bypass hole state of the intermediate plate in the first variable displacement state provided in an embodiment of the present invention; Figure 8 is a schematic diagram of the cooperation relationship of the adaptive variable displacement mechanism in the second variable displacement state provided in an embodiment of the present invention; Figure 9 is a schematic diagram of the bypass hole state of the intermediate plate in the second variable displacement state provided in an embodiment of the present invention.

[0020] Among them, 10-cylinder; 11-cylinder head; 20-intermediate plate; 21-bypass hole; 22-return hole; 23-annular motion channel; 24-pressure tapping hole; 25-thrust structure; 30-arc motion assembly; 40-resistance assembly. Detailed Implementation

[0021] Exemplary embodiments will now be described more fully with reference to the accompanying drawings. However, these exemplary embodiments can be implemented in many forms and should not be construed as limited to the embodiments set forth herein; rather, these embodiments are provided so that the invention will be thorough and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art. The same reference numerals in the drawings denote the same or similar structures, and therefore repeated descriptions of them will be omitted. The words “or” and “or” in the specification may mean “and” or “or”. Although terms such as “above,” “below,” and “between” may be used in this specification to describe different exemplary features and elements of the invention, these are used herein only for convenience, such as according to the orientation of the examples in the drawings. Nothing in this specification should be construed as requiring a specific three-dimensional orientation of the structure to fall within the scope of the invention. Although terms such as “first” or “second” are used in this specification to denote certain features, they are merely indicative of function and not as a limitation on the number or importance of specific features.

[0022] In this invention, axial direction refers to the extension direction parallel to the rotation center line of the compressor crankshaft or drive shaft, corresponding to the vertical direction in a conventional vertical compressor; radial direction refers to the direction perpendicular to the axial direction and radiating outward from the rotation center or converging inward from the outside; circumferential direction refers to the tangential direction of the circumference around the axial direction. Based on the flow path of the refrigerant, upstream and downstream are defined with reference to the flow direction of the refrigerant entering from the intake port, being compressed, and exiting from the exhaust port. For example, the intake port is located upstream of the bypass port. Inner and outer directions refer to directions closer to or farther from the cylinder center axis, respectively.

[0023] An intermediate plate refers to a plate-like component disposed between the cylinder and the end cap, such as a cylinder head, and is structurally independent of the cylinder body and the end cap body. An arc-shaped motion assembly includes interconnected or integrally formed arc-shaped sliders and arc-shaped slip rings. The arc-shaped slip ring is a non-closed arc-shaped structure with a notch formed in the circumferential direction, such as an integrally formed C-shaped slip ring structure. A resistance assembly refers to a physical mechanism that provides return resistance, including helical springs, rubber elastic elements, magnetic repulsion components, or shape memory alloy components. A thrust structure refers to a feature that physically limits the motion assembly, including bosses, blocks, or abrupt changes in the flow channel cross-section. Connections or links mentioned in the specification include mechanical fixed connections and fluid communication relationships.

[0024] Based on the operating characteristics of variable frequency air conditioning systems, air conditioning capacity The difference between the condensing pressure and the evaporating pressure of an air conditioner is the difference between the compressor's suction and discharge pressures. Compressor displacement and compressor speed There is a functional relationship between them. When the compressor speed... When determined, the system's intake and exhaust pressure difference Therefore, it is determined. In this embodiment, the intake and exhaust pressure difference... With rotational speed There is a positive correlation between them, that is, rotational speed The larger the pressure difference between intake and exhaust, the greater the pressure difference. The larger.

[0025] Based on the above physical laws, the adaptive variable displacement mechanism is configured to be driven by pressure difference. Let the intake pressure be denoted as... The exhaust pressure is recorded as The pressure-bearing area of ​​the arc-shaped moving component that withstands the exhaust pressure is denoted as... The pressure difference thrust experienced by the arc-shaped motion component The following relationship must be satisfied:

[0026] At the same time, the resistance component provides reverse resistance to the arc-shaped motion component. During compressor operation, the position of the arc-shaped moving component depends on the pressure differential thrust. and reverse resistance The mechanical equilibrium state. When external operating conditions change, causing the exhaust pressure to... and inhalation pressure When the pressure difference thrust changes Consequently, the motion of the driven arc-shaped component changes, altering the deformation of the resistance component. Until a new equilibrium position is reached.

[0027] The change in this equilibrium position directly determines the distribution angle of the exposed bypass holes of the arc-shaped motion component in the cylinder circumferential direction. Different bypass hole angles correspond to different variable displacement ratios. This invention achieves multi-stage variable displacement ratio adjustment by changing the angle of the exposed bypass holes, providing a larger variable capacity under conditions of lower capacity requirements, thereby increasing the compressor's operating speed; simultaneously, it can match the corresponding variable displacement ratio according to different capacity requirements, realizing adaptive continuous or quasi-continuous adjustment of the compressor displacement according to operating conditions.

[0028] Figures 1 to 4 illustrate the specific structure of a multi-stage variable displacement compressor. The multi-stage variable displacement compressor includes a housing and a pump assembly fixed within the housing. The pump assembly mainly consists of a cylinder 10, a main bearing, a cylinder head 11, and an intermediate plate 20 located between the cylinder 10 and the cylinder head 11. The cylinder 10 has an inner bore extending through both axial ends. The main bearing and the cylinder head 11 are respectively sealed at both axial end faces of the cylinder 10, defining a closed cylinder chamber within the cylinder 10. An eccentric portion of the crankshaft is located within the cylinder chamber, and an annular piston is fitted onto the eccentric portion. A vane groove is provided within the cylinder 10, with vanes positioned within the vane groove and abutting against the outer wall of the annular piston, dividing the cylinder chamber into a low-pressure intake chamber and a high-pressure compression chamber. The refrigerant compressed by the cylinder 10 is discharged into the inner cavity of the housing.

[0029] The intermediate plate 20 is an independent plate-shaped component, coaxially sandwiched between the cylinder 10 and the cylinder head 11. Multiple bypass holes 21 are circumferentially distributed through the intermediate plate 20. One end of each bypass hole 21 is located within the inner cavity of the cylinder 10, connecting to the compression chamber of the cylinder 10. In a radial position, the multiple bypass holes 21 are located within the region between the movement trajectory of the outer ring of the annular piston within the cylinder 10 and the movement trajectory of the inner ring of the annular piston within the cylinder 10.

[0030] Center of the sliding vane groove of cylinder 10 The reference angle, denoted as the angle of rotation along the direction of the intake port, is denoted as... The distribution angle range of multiple bypass holes 21 satisfy In the variable-capacity mode of the compressor, some bypass holes 21 are open within the annular motion channel 23. Before the annular piston in the cylinder 10 rotates past the open bypass hole 21, the gas entering the cylinder chamber from the intake port flows back through the bypass hole 21. After the annular piston rotates past the open bypass hole 21, the cavity formed by the annular piston, the sliding vane, and the cylinder wall near the cylinder exhaust port is closed and compression begins. The larger the angle at which the open bypass holes 21 are distributed, the smaller the volume of the cavity that is ultimately closed and enters the compression state, the smaller the actual amount of refrigerant compressed, the smaller the compressor displacement, and the larger the corresponding variable-capacity ratio.

[0031] An annular motion channel 23 is provided on the side of the cylinder head 11 facing the intermediate plate 20. The intermediate plate 20 fits tightly against the cylinder head 11, covering the annular motion channel 23 to form a control cavity. The other ends of the multiple bypass holes 21 project into the annular motion channel 23.

[0032] The annular motion channel 23 has a first circumferential section and a second circumferential section. The first circumferential section is an arc-shaped motion groove, with a return hole 22 at one end and a pressure tapping hole 24 at the other end. The second circumferential section is a cut-off section, located between the return hole 22 and the pressure tapping hole 24, separating the return hole 22 and the pressure tapping hole 24. The cut-off section is essentially a solid wall surface on the lower cylinder head 11 body without the arc-shaped motion groove. This solid wall surface physically forms an airtight isolation between the high-pressure pressure tapping hole 24 and the low-pressure return hole 22, preventing a direct fluid short circuit between the exhaust pressure and the intake pressure within the annular motion channel 23.

[0033] The pressure-inlet hole 24 penetrates the cylinder head 11 in an open shape, connecting to the inner cavity of the compressor housing, forming a pressure-inlet channel for introducing exhaust pressure. The return hole 22 connects to the intake hole, forming a return channel for introducing intake pressure. Specifically, the return channel includes an axial guide groove formed inside or on the side wall of the cylinder 10 body. The return hole 22 is aligned with and connects to the axial guide groove in the axial assembly position, thereby communicating with the radial intake hole of the cylinder 10 to form a sealed low-pressure return path. Thus, one end of the annular motion channel 23 introduces the intake pressure of the multi-stage variable displacement compressor through the return channel, and the other end introduces the exhaust pressure of the multi-stage variable displacement compressor through the pressure-inlet channel.

[0034] The arc-shaped motion component 30 is slidably fitted with a clearance within the annular motion channel 23 disposed in the cylinder head 11, and can shield a portion of the annular motion channel 23. The arc-shaped motion component 30 includes an arc-shaped slider and an arc-shaped slip ring, and the bypass hole 21 is configured to be exposed to the annular motion channel 23 through a notch in the arc-shaped slip ring. In terms of overall force, the arc-shaped motion component 30 is configured to bear exhaust pressure and intake pressure at its two ends respectively. The arc-shaped slider is located in the internal space of the annular motion channel 23, with one end connected to the resistance component 40 and bearing intake pressure, and the other end bearing exhaust pressure. The arc-shaped slip ring is a non-closed arc-shaped structure with a notch formed in the circumferential direction, the notch referring to the physical clearance space formed between the two circumferential ends of the arc-shaped slip ring. The circumferential span angle of the notch is configured to be equal to or greater than the diameter of at least one of the bypass holes 21, such that when the arc-shaped slip ring slides circumferentially within the annular motion channel 23, the bypass hole 21 swept by the notch is removed from the solid shield of the arc-shaped slip ring and directly exposed in the annular motion channel 23 to form a conductive flow path. The arc-shaped slip ring moves synchronously with the arc-shaped slider, conforming to the lower surface of the intermediate plate 20 to cover the annular motion channel 23. The bypass hole 21 is configured to be exposed in the annular motion channel 23 through the notch of the arc-shaped slip ring.

[0035] The arc-shaped motion component 30 can be a one-piece molded component or a modular assembly structure. When a modular assembly structure is used, the arc-shaped slider used to withstand the pressure difference and the resistance of the resistance component 40, and the arc-shaped slip ring used to block the bypass hole 21, are manufactured as two separate arc-shaped parts. The arc-shaped slider and the arc-shaped slip ring are fixed together by riveting, welding, snap-fit ​​connection, or pin connection. The modular design allows the arc-shaped slider and the arc-shaped slip ring to be made of different materials. For example, the arc-shaped slider can be made of high-strength steel to withstand stress, while the arc-shaped slip ring can be made of a self-lubricating material to reduce friction.

[0036] When a split assembly structure is adopted, the arc-shaped slider is constructed as a cylindrical arc-shaped body with a certain axial height, which is housed within the annular motion channel 23 and serves as a pressure-bearing entity; the arc-shaped slip ring is constructed as a flat, sheet-like arc-shaped body. The axial end face of the arc-shaped slider is provided with a positioning boss or fitting groove, and the corresponding surface of the arc-shaped slip ring is provided with a mating surface. The two are overlapped axially and fixed as a rigid whole by riveting, welding, snap-fit ​​connection, or pin connection. This assembly method ensures that when the arc-shaped slider is pressed and slides circumferentially within the annular motion channel 23, it can rigidly drive the arc-shaped slip ring to slide synchronously circumferentially on the lower surface of the intermediate plate 20 through mechanical force, and the connection does not interfere with the clearance fit between the arc-shaped motion component 30 and the annular motion channel 23.

[0037] The resistance component 40 is disposed within the annular motion channel 23 and acts on the arc-shaped motion component 30. Taking a helical spring as an example, the resistance component 40 is housed within the annular motion channel 23. One end of the helical spring abuts against the circumferential end of the first circumferential segment of the annular motion channel 23, and the other end abuts against the circumferential end face of the arc-shaped slider of the arc-shaped motion component 30, thereby applying a reset resistance towards the pressure-inducing hole 24 to the arc-shaped motion component 30. Besides the helical spring, the resistance component 40 is selected from one or a combination of rubber elastic elements, magnetic repulsion components, or shape memory alloy components. When the resistance component 40 uses a magnetic repulsion component, the magnetic repulsion component includes a first magnetic element and a second magnetic element. The first magnetic element is located on the end face of the annular motion channel 23 on the side where the suction pressure is introduced, and the second magnetic element is located on the arc-shaped motion component 30. The polarities of the opposing sides of the first and second magnetic elements are the same.

[0038] Figures 4 to 9 illustrate the dynamic adjustment process of the adaptive variable capacity mechanism as the load of the multi-stage variable capacity compressor changes.

[0039] When the exhaust pressure exceeds a preset threshold, the pressure difference thrust overcomes the resistance of the resistance component 40, pushing the arc-shaped motion component 30 to slide away from the pressure inlet 24 to the first position. In the first position, the arc-shaped slip ring of the arc-shaped motion component 30 completely covers the multiple bypass holes 21. The refrigerant in the compression chamber of cylinder 10 cannot flow back through the bypass holes 21, and the multi-stage variable displacement compressor is in full-displacement operation.

[0040] When the exhaust pressure decreases, the pressure difference thrust decreases. The arc-shaped motion component 30 moves in the opposite direction under the action of the resistance component 40. As the arc-shaped motion component 30 retracts circumferentially, the bypass hole 21 is exposed through the notch of the arc-shaped slip ring. Part of the refrigerant gas in the intake phase of the cylinder 10 passes through the exposed bypass hole 21 into the annular motion channel 23, then flows along the annular motion channel 23 to the return hole 22, and is discharged to the intake port side through the return hole 22.

[0041] In one embodiment, the bypass holes 21 are evenly spaced circumferentially. As the arc-shaped motion component 30 begins to retract, the number of exposed bypass holes 21 gradually increases. When the notch of the arc-shaped slip ring is completely within the angular range covered by the multiple bypass holes 21, the number of bypass holes 21 exposed by the notch is the same each time, and the return area remains the same. As the retraction position of the arc-shaped motion component 30 changes, the angular position of the exposed bypass holes 21 in the circumferential direction changes. Before the annular piston in the cylinder 10 rotates past the bypass hole 21 in the open state, the gas returns through the bypass hole 21; after the annular piston rotates past the bypass hole 21 in the open state, the cylinder 10 cavity is closed and compression begins. The angular position of the exposed bypass hole 21 determines the starting angle of compression in the cylinder 10. The larger the angle of the bypass hole 21 from the intake port, the smaller the cavity that is ultimately closed and enters the compression state, the smaller the actual amount of refrigerant compressed, the smaller the displacement, and the larger the corresponding volume ratio.

[0042] In existing technologies, one of several bypass holes is discretely selected and opened to obtain a corresponding variable capacity ratio, with the number of variable capacity ratios being the same as the number of bypass holes. In this invention, however, the notch exposes multiple bypass holes 21 at once, and the angle of the exposed bypass holes 21 changes as the arc-shaped slip ring rotates. The number of combinations of exposed bypass holes 21 within the notch of this invention is greater than the number of bypass holes 21, resulting in a significantly greater number of variable capacity ratios than the number of bypass holes 21.

[0043] When the multi-stage variable displacement compressor stops, the discharge pressure and intake pressure quickly reach equilibrium, and the pressure difference disappears. The resistance component 40 pushes the arc-shaped motion component 30 to reset. A thrust structure 25 is provided on the side of the arc-shaped motion groove in the first circumferential section near the pressure tap 24. When the resistance component 40 pushes the arc-shaped motion component 30 to reset, the thrust structure 25 restricts the extreme position of the arc-shaped motion component 30, so that an intake gap is maintained between the arc-shaped motion component 30 and the pressure tap 24 to establish the supply and discharge pressure. The intake gap ensures that when the multi-stage variable displacement compressor starts again, high-pressure gas can enter the force-bearing end of the arc-shaped motion component 30 to establish the initial thrust required to push the arc-shaped motion component 30, avoiding pneumatic lock-up.

[0044] The thrust structure 25 is constructed as an integral limiting step on the cylinder head 11. In an alternative, the thrust structure 25 is constructed as a limiting pin, which is press-fitted into the pin hole of the cylinder head 11 and protrudes into the annular movement channel 23; or, the thrust structure 25 is constructed as a thrust screw, which is fixed to the cylinder head 11 by a threaded connection.

[0045] The cylinder 10, intermediate plate 20, and cylinder head 11 are connected by fastening bolts. In other implementations, the cylinder 10, intermediate plate 20, and cylinder head 11 are configured to be fixedly connected by laser welding or argon arc welding; or configured to be assembled into the housing by interference fit, using the radial contraction force of the housing to achieve axial compression and fixation between the components.

[0046] The multi-stage variable displacement compressor employs a circumferential sliding opening method. As the arc-shaped slip ring of the arc-shaped motion component 30 rotates with the pressure difference and the notch edge slides past the bypass hole 21, the exposed area of ​​a single bypass hole 21 gradually increases with the rotation angle. This gradual unloading process reduces airflow impact noise and pressure pulsation generated when the orifice of the variable displacement structure opens, thus reducing noise and vibration during the variable displacement switching process of the multi-stage variable displacement compressor. Furthermore, bypass holes 21 with different distribution angles correspond to different variable displacement ratios. In the configuration where a single bypass hole 21 is selectively opened, the number of variable displacement ratios obtained is the same as the number of bypass holes 21; in the circumferential sliding configuration of the multi-stage variable displacement compressor, the notch of the arc-shaped slip ring continuously or quasi-continuously exposes bypass holes 21 at different angles during rotation, resulting in a greater number of variable displacement ratios achieved by the multi-stage variable displacement compressor than the number of bypass holes 21.

[0047] This invention also provides an air conditioning system. Under low-load conditions, the adaptive variable-capacity mechanism reduces the displacement of the multi-stage variable-capacity compressor to increase the motor speed. The increased speed allows the motor of the multi-stage variable-capacity compressor to operate within a preset high-efficiency speed range, reducing power consumption; simultaneously, the operating speed avoids the low-frequency resonance region. The adaptive variable-capacity mechanism achieves displacement adjustment without the need for additional electrical control harnesses and drive modules, reducing the system's footprint.

[0048] The above are merely preferred embodiments of the present invention and are 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.

Claims

1. A multi-stage variable displacement compressor, comprising a cylinder and a cylinder cover covering the end face of the cylinder, wherein the cylinder is provided with an intake port, characterized in that, It also includes an adaptive variable displacement mechanism, which comprises: an intermediate plate disposed between the cylinder and the cylinder head, the intermediate plate having a plurality of bypass holes distributed circumferentially; an annular motion channel being formed on the side of the cylinder head facing the intermediate plate, one end of the plurality of bypass holes being located in the inner cavity of the cylinder, and the other end projecting into the annular motion channel; an arc-shaped motion component, clearance-fitted within the annular motion channel, capable of shielding a portion of the annular motion channel; and a resistance component disposed within the annular motion channel and acting on the arc-shaped motion component, used to apply reset resistance to the arc-shaped motion component; one end of the annular motion channel introduces the compressor's intake pressure through a return channel, and the other end introduces the compressor's exhaust pressure through a pressure-inducing channel; the arc-shaped motion component is configured to bear the exhaust pressure and the intake pressure at both ends respectively, and slides circumferentially along the annular motion channel under the pressure difference between the exhaust pressure and the intake pressure and the action of the resistance component, thereby blocking or connecting the flow path between one or more of the plurality of bypass holes and the intake hole.

2. The multi-stage variable displacement compressor according to claim 1, characterized in that, The arc-shaped motion component includes an arc-shaped slider and an arc-shaped slip ring that are connected to each other or integrally formed; one end of the arc-shaped slider is connected to the resistance component and bears the intake pressure, while the other end bears the exhaust pressure. The arc-shaped slip ring is a non-closed arc-shaped structure with a notch in the circumferential direction. The arc-shaped slip ring moves synchronously with the arc-shaped slider to fit the lower surface of the intermediate plate to cover the annular motion channel. One or more of the bypass holes can be exposed to the annular motion channel through the notch of the arc-shaped slip ring.

3. The multi-stage variable-capacity compressor according to claim 1, characterized in that, The annular motion channel has a first circumferential section and a second circumferential section. The first circumferential section is an arc-shaped motion groove, and a return hole is provided at one end of the arc-shaped motion groove for connecting the return channel. The other end is provided with a pressure-guiding hole for connecting to the pressure-guiding channel; The second circumferential section is a cut-off section, which is located between the reflux hole and the pressure tapping hole to isolate the reflux hole and the pressure tapping hole.

4. The multi-stage variable displacement compressor according to claim 3, characterized in that, A thrust-stop structure is provided on the side of the motion groove near the pressure-inlet hole. The thrust-stop structure is configured to limit the extreme position of the arc-shaped motion component when the resistance component pushes the arc-shaped motion component to reset, so that an intake gap is maintained between the arc-shaped motion component and the pressure-inlet hole for the exhaust pressure to be established.

5. The multi-stage variable displacement compressor according to claim 4, characterized in that, The thrust-stop structure is constructed as a limiting step protruding into the annular motion channel.

6. The multi-stage variable-capacity compressor according to claim 1, characterized in that, With the center of the cylinder's vane groove as the 0° reference, the distribution angle range α of the multiple bypass holes satisfies: 60° < α < 210°.

7. The multi-stage variable displacement compressor according to claim 3, characterized in that, The refrigerant compressed by the cylinder is discharged into the inner cavity of the housing of the multi-stage variable capacity compressor. The pressure inlet is open through the cylinder head and connects to the inner cavity of the housing of the multi-stage variable capacity compressor. The return outlet is connected to the suction port.

8. The multi-stage variable displacement compressor according to claim 1, characterized in that, The cylinder is equipped with an annular piston, and the plurality of bypass holes are located in the area between the movement trajectory of the outer ring of the piston within the cylinder and the movement trajectory of the inner ring of the piston within the cylinder.

9. The multi-stage variable displacement compressor according to claim 1, characterized in that, The resistance component is selected from one or a combination of helical springs, rubber elastic elements, magnetic repulsion components, or shape memory alloy components.

10. An air conditioning system, characterized in that, Including the multi-stage variable capacity compressor as described in any one of claims 1 to 9.

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