Compressor

Abstract

The invention provides a compressor, a volume-variable structure is arranged in a pump body assembly of the compressor, and the volume-variable structure comprises a bypass hole, a movement channel and a backflow channel; the first end of the movement channel communicates with the backflow channel, the second end of the movement channel communicates with the exhaust pressure side of the compressor, a reset piece and a movement piece are arranged in the movement channel, and the two ends of the reset piece abut against the wall face of the movement channel and the movement piece correspondingly; one end of the bypass hole is communicated with the motion channel, and the other end is communicated with an inner cavity of the cylinder; one end of the backflow channel is communicated with the suction pressure side of the compressor; the two sides of the moving part are subjected to air suction pressure and air exhaust pressure respectively, and the moving part can move in the moving channel in a reciprocating mode under the action of the pressure difference of the two sides and the reset part. The moving part is in a first state and covers the bypass hole, so that the bypass hole is not communicated with the backflow channel; and the moving part is in a second state and avoids the bypass hole, so that the moving part is communicated with the backflow channel.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and more specifically, to a compressor. Background Technology

[0002] Against the backdrop of the deepening global energy conservation and emission reduction policies and the ever-increasing demand from users for air conditioning comfort, air conditioning compressors are increasingly being used in low-frequency operation scenarios, and wide-frequency adjustment and high efficiency and low consumption have become inevitable trends in technological development.

[0003] However, rotary compressors face a series of technical challenges under low-frequency operating conditions: First, the efficiency of the motor decreases significantly in the low-speed range, resulting in reduced system energy efficiency; second, the speed fluctuation range increases, affecting the smoothness of operation and control accuracy; at the same time, the oil supply of the lubrication system decreases as the speed decreases, resulting in insufficient lubrication of key friction pairs and exacerbating the risk of wear; in addition, insufficient oil pressure on the back of the blades causes the blades to be unable to keep in close contact with the roller surface, resulting in periodic impacts and causing a "ticking" noise, which not only affects the user experience but also restricts the reliability and lifespan of the compressor.

[0004] Variable capacity compressor technology can indirectly increase the compressor speed by reducing the compressor capacity, thus improving the compressor's operation at low frequencies. Existing variable capacity technologies require the addition of valves, additional flow channels, and corresponding sensors inside or outside the compressor housing and piping. The system uses complex logic algorithms to control valve opening and closing to achieve variable capacity, which increases the system's complexity and cost.

[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 compressor with an adaptive variable-capacity structure that requires no system control. The variable-capacity structure is closed under high pressure differential conditions and automatically activated under low pressure differential conditions, thereby increasing compressor speed and efficiency, and avoiding various problems that occur when the compressor operates at low frequencies.

[0007] Specifically, the present invention provides a compressor in which a variable displacement structure is provided in the pump body assembly of the compressor, the variable displacement structure including a bypass hole, a motion channel and a return channel; The first end of the motion channel is connected to the return channel, and the second end is connected to the exhaust pressure side of the compressor. A reset component and a moving component are provided in the motion channel. The two ends of the reset component abut against the wall of the motion channel and the moving component, respectively. One end of the bypass hole is connected to the motion channel, and the other end is connected to the inner cavity of the cylinder; One end of the return channel is connected to the suction pressure side of the compressor; The moving part is subjected to inhalation pressure and exhaust pressure on both sides respectively. Under the action of the pressure difference on both sides and the reset part, the moving part can reciprocate within the moving channel. The moving part is in the first state, covering the bypass hole, so that the bypass hole is not connected to the return channel; The moving part is in the second state, avoiding the bypass hole, so that the bypass hole is connected to the return channel.

[0008] According to some embodiments of the present invention, the reset member is an elastic member, which is one of a spring, rubber, and shape memory alloy components.

[0009] According to some embodiments of the present invention, the reset member includes a first magnetic member and a second magnetic member, the first magnetic member being located on the wall of the motion channel, the second magnetic member being located on the motion member, and the polarity of the opposite sides of the first magnetic member and the second magnetic member being the same.

[0010] According to some embodiments of the present invention, the refrigerant compressed by the pump assembly is discharged into the inner cavity of the compressor housing, the discharge pressure side including the inner cavity of the housing.

[0011] According to some embodiments of the present invention, the second end of the motion channel is an open end.

[0012] According to some embodiments of the present invention, the intake pressure side includes a cylinder intake port, a reservoir, or an intake pipe between the reservoir and the cylinder intake port.

[0013] According to some embodiments of the present invention, the moving part avoids the bypass hole in its initial position, and the bypass hole is connected to the return channel through the moving channel.

[0014] According to some embodiments of the present invention, the pressure difference experienced by the moving part when it is at a critical position that is about to close the bypass hole is set as a first pressure difference threshold P1, and the pressure difference experienced by the moving part when it is at a critical position that is about to avoid the bypass hole is set as a second pressure difference threshold P2. When the pressure difference between the compressor's suction pressure Ps and discharge pressure Pd When the pressure difference exceeds the first differential pressure threshold P1, the moving part moves towards the direction of the return channel and gradually covers the bypass hole, causing the bypass hole to disconnect from the moving channel. When the pressure difference between the compressor's suction pressure Ps and discharge pressure Pd When the pressure difference is not greater than the second differential pressure threshold P2, the moving part moves away from the return channel and gradually avoids the bypass hole, so that the bypass hole is connected to the moving channel.

[0015] According to some embodiments of the present invention, limiting members are provided on both sides of the moving member to limit the movement stroke of the moving member within the movement channel.

[0016] According to some embodiments of the present invention, the motion channel is disposed on the cylinder of the pump body assembly, or on the cylinder cover covering the cylinder end face.

[0017] The variable-capacity structure of the compressor in this invention is adaptive. When the load of the air conditioning system increases and the demand on the compressor's capacity increases, the compressor gradually operates at full capacity. Conversely, under low-pressure differential conditions where the demand on the compressor's capacity decreases, a variable-capacity mode is activated. In this mode, before the compressor piston rotates to the bypass port, the cylinder's inner cavity is connected to the cylinder's suction port through the bypass port, allowing some refrigerant to flow back. After the piston rotates past the bypass port, the actual amount of refrigerant compressed in the cavity formed by the piston, vanes, and the cylinder wall near the cylinder's exhaust port decreases; in other words, the compression cavity becomes smaller, and the displacement decreases. Although the system is in a low-demand state at this time, the controller will still increase the speed to maintain this low-demand state, indirectly ensuring that the compressor maintains a certain high speed during low-demand operation, thus avoiding various problems that occur when the compressor operates at low frequencies. Furthermore, this variable-capacity structure automatically opens or closes under the pressure difference between the compressor's suction and exhaust pressures, eliminating the need for external control components such as valves, thus reducing system complexity and cost. Attached Figure Description

[0018] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application. 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. It is obvious that the drawings described below are merely some embodiments of the invention, and those skilled in the art can obtain other drawings based on these drawings without inventive effort. Furthermore, the drawings are merely illustrative diagrams of this disclosure and are not necessarily drawn to scale. The same reference numerals in the drawings denote the same or similar parts, and therefore repeated descriptions of them will be omitted. Some block diagrams shown in the drawings are functional entities and do not necessarily correspond to physically or logically independent entities.

[0019] Figure 1 The difference between the intake and exhaust pressures of a 1.5 horsepower compressor measured in the experiment. A graph showing the relationship between cooling capacity and other parameters; Figure 2 The difference between the intake and exhaust pressures of a 1.5 horsepower compressor measured in the experiment. A graph showing the relationship between the compressor speed and the compressor rotation speed; Figure 3 and Figure 4 These are partial structural schematic diagrams of the compressor under different states according to the first embodiment of the present invention; Figure 5 This is a top view of the lower cylinder head of the compressor according to the first embodiment of the present invention; Figure 6 This is a partial structural schematic diagram of the compressor according to the second embodiment of the present invention; Figure 7 This is a partial structural schematic diagram of the compressor according to the third embodiment of the present invention; Figure 8 This is a schematic diagram of the cylinder structure of the compressor according to the fourth embodiment of the present invention; Figure 9 This is a schematic diagram of the compressor according to the fifth embodiment of the present invention. Detailed Implementation

[0020] The following specific examples illustrate the implementation of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed herein. The present invention can also be implemented or applied through other different specific embodiments, and various details in the present invention can be modified or changed according to different viewpoints and application systems without departing from the spirit of the present invention. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of the present invention can be combined with each other.

[0021] The present invention will now be described in detail with reference to the accompanying drawings, so that those skilled in the art can readily implement it. The present invention can be embodied in many different forms and is not limited to the embodiments described herein.

[0022] In the representation of this invention, the terms "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics represented in connection with that embodiment or example, which are included in at least one embodiment or example of the invention. Furthermore, the specific features, structures, materials, or characteristics represented may be combined in any suitable manner in one or more embodiments or examples. Moreover, those skilled in the art can combine and integrate different embodiments or examples represented in this invention, as well as features of different embodiments or examples, without contradiction.

[0023] To clearly illustrate the present invention, components unrelated to the description are omitted, and the same or similar constituent elements throughout the specification are given the same reference numerals.

[0024] Throughout this specification, when it is said that a device is "connected" to another device, this includes not only "direct connection" but also "indirect connection" by placing other components in between. Furthermore, when it is said that a device "comprises" a certain constituent element, unless otherwise stated otherwise, this does not exclude other constituent elements, but rather implies that other constituent elements may be included.

[0025] When we say that a device is "above" another device, this can mean that it is directly above the other device, or it can mean that other devices are present in between. Conversely, when we say that a device is "directly" "above" another device, there are no other devices present in between.

[0026] Although the terms first, second, etc., are used in some instances herein to refer to various elements, these elements should not be limited by these terms. These terms are used only to distinguish one element from another. For example, first interface and second interface, etc., are used. Furthermore, as used herein, the singular forms “a,” “an,” and “the” are intended to also include the plural forms unless the context indicates otherwise. It should be further understood that the terms “comprising,” “including,” indicate the presence of features, steps, operations, elements, components, items, kinds, and / or groups, but do not exclude the presence, occurrence, or addition of one or more other features, steps, operations, elements, components, items, kinds, and / or groups. The terms “or” and “and / or” as used herein are interpreted as inclusive, or mean any one or any combination thereof. Thus, “A, B, or C” or “A, B, and / or C” means “any one of: A; B; C; A and B; A and C; B and C; A, B, and C.” Exceptions to this definition will only occur if the combination of elements, functions, steps, or operations is inherently mutually exclusive in some way.

[0027] The technical terms used herein are for reference only to specific embodiments and are not intended to limit the invention. The singular form used herein includes the plural form unless the statement explicitly indicates otherwise. The word "comprising" as used in this specification means to specify a particular characteristic, region, integer, step, operation, element, and / or component, and does not exclude the presence or addition of other characteristics, regions, integers, steps, operations, elements, and / or components.

[0028] Unless otherwise defined in this application, all terms, including technical and scientific terms as used herein, shall have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. Terms defined in commonly used dictionaries shall be further interpreted as having a meaning consistent with relevant technical literature and the content of this present instruction, and shall not be over-interpreted as having an ideal or overly formulaic meaning unless otherwise defined.

[0029] The compressor of the present invention will be further described below with reference to the accompanying drawings and specific embodiments. It should be understood that the specific embodiments are not intended to limit the scope of protection of the present invention.

[0030] For a given variable frequency air conditioning system, the following functional relationship exists. , And thus Where Q represents air conditioning capacity, Let A be the difference between the condensing and evaporating pressures of the air conditioner (i.e., the difference between the compressor's suction and discharge pressures), A be the compressor displacement, and n be the compressor speed when the air conditioner's capacity (cooling capacity) is Q. When the compressor speed n is fixed, the condensing-evaporating pressure difference of the air conditioner... It was also confirmed, and data research and analysis revealed... and as well as The functional relationship between them is very close to that of a linear function. The larger the speed, the higher the rotation speed. The larger the pressure difference, the greater the pressure difference. The larger it is, the more specific it is. Figure 1 and Figure 2 As shown.

[0031] Based on the above principles, the present invention provides a compressor, wherein the pump body assembly of the compressor is provided with a variable displacement structure including a bypass hole, a motion channel and a return channel; The first end of the motion channel is connected to the return channel, and the second end is connected to the exhaust pressure side of the compressor. A reset component and a moving component are provided in the motion channel. The two ends of the reset component abut against the wall of the motion channel and the moving component, respectively. The moving component can reciprocate within the motion channel. One end of the bypass hole is connected to the motion channel, and the other end is connected to the inner cavity of the cylinder; the other end of the return channel is connected to the suction pressure side of the compressor; it should be noted that the refrigerant compressed by the pump body assembly is discharged into the inner cavity of the compressor housing, the exhaust pressure side includes the inner cavity of the housing, and the suction pressure side includes the cylinder suction port, the liquid receiver, or the suction pipe between the liquid receiver and the cylinder suction port. The moving part is in the first state, and the moving part covers the bypass hole, so that the bypass hole is not connected to the return channel; The moving part is in the second state, and the moving part avoids the bypass hole, so that the bypass hole is connected to the return channel.

[0032] The compressor includes the aforementioned variable displacement structure and pump body assembly. Figure 3 and Figure 4These are partial structural diagrams of the compressor in different states according to the first embodiment of the present invention. The pump body assembly includes a cylinder 3, an upper cylinder cover 1 and a lower cylinder cover 2. The upper cylinder cover 1 and the lower cylinder cover 2 are respectively disposed at both ends of the cylinder 3. The cylinder 3, the upper cylinder cover 1 and the lower cylinder cover 2 enclose a accommodating space, which can accommodate the eccentric part of the crankshaft 4, the piston 5 and the blade 6 and other components.

[0033] The motion channel 9 can be located inside the upper or lower cylinder head, or it can be located on the cylinder. In the first embodiment, the motion channel 9 can be located inside the lower cylinder head 2, and the second end of the motion channel 9 is an open end, see... Figure 5 Specifically, the axis of the motion channel 9 can be parallel to the end face of the lower cylinder head 2. The reset member 941 is an elastic member, which can be one of the components that can provide resistance, such as a spring, rubber, or shape memory alloy component. One end of the reset member 941 abuts against the wall of the motion channel 9, and the other end abuts against the motion member 942. The outer periphery of the motion member 942 fits against the inner wall of the motion channel 9. The open end of the motion channel 9 is connected to the exhaust pressure side (high pressure side) of the compressor, specifically, it is connected to the inside of the compressor housing.

[0034] A bypass hole 92 is disposed within the lower cylinder head 2, and the two ends of the return channel are respectively connected to the motion channel and the intake pressure side of the compressor. The return channel includes a first return hole 93 disposed in the lower cylinder head 2 and a second return hole 931 disposed in the cylinder 3. The first return hole 93 is disposed at the first end of the motion channel 9, and the two ends of the second return hole 931 are respectively connected to the first return hole 93 and the inner cavity of the cylinder. Preferably, the second return hole 931 is located inside the cylinder on the side closer to the intake port.

[0035] The compressor's suction pressure is P s The exhaust pressure is P d The pressure-bearing area of ​​moving part 942 is D. Then the pressure difference... P s -P d The pressure difference force at one end of the moving part 942 (the end closest to the opening of the motion channel) is F1, and the pressure difference force F1 = D.

[0036] In the first embodiment, the reset member is an elastic member, such as the reset member 941 being a helical spring. The other end of the moving member 942 is subjected to a force F2, which is the pressure exerted by the helical spring. When the moving member 942 is in the initial position, the bypass hole 92 is connected to the return channel through the movement channel 9, so that the moving member 942 will not be exposed in the bypass hole 92 when it approaches the second end of the movement channel. Figure 4 When external operating conditions change, P s P dThe deformation of the reset component also changes, and the change in the deformation of the reset component causes the position of the moving component in the motion channel to change, thereby controlling the connection state between the bypass hole and the motion channel, or in other words, controlling the opening and closing state of the bypass hole.

[0037] In practical applications, the pressure difference experienced by the moving part 942 when it is at a critical position about to close the bypass hole is set as the first pressure difference threshold P1, and the pressure difference experienced by the moving part when it is at a critical position about to avoid the bypass hole is set as the second pressure difference threshold P2. The pressure difference between the compressor's suction pressure Ps and discharge pressure Pd... When the pressure difference exceeds the first differential pressure threshold P1, the moving part 942 moves towards the return channel, gradually covering the bypass hole 92, thus disconnecting the bypass hole 92 from the moving channel. When the pressure difference between the compressor's suction pressure Ps and discharge pressure Pd... When the pressure difference is not greater than the second differential pressure threshold P2, the moving part 942 moves away from the return channel to gradually avoid the bypass hole 92, so that the bypass hole 92 is connected to the moving channel. Figure 3 As shown, the compressed gas passes through the bypass hole 92, the motion channel 9, the first return hole 93, and the second return hole 931 to the suction side. The compressor maintains a variable displacement state. In the variable displacement state, before the compressor piston rotates to the bypass hole, the refrigerant connects to the cylinder suction hole through the bypass hole, so that part of the refrigerant entering the cylinder flows back to the suction hole. After the piston rotates past the bypass hole, the gas in the compression chamber begins to be compressed. The actual amount of refrigerant drawn into the compressor decreases, and the displacement decreases. Although the system is in a low demand state at this time, the controller will also control the speed to increase in order to achieve this low demand state, indirectly achieving that the compressor maintains a certain high speed in the low demand state, avoiding various problems that occur when the compressor operates at low frequency.

[0038] The above control requirements can be met by designing the bearing area D (cross-sectional area of ​​the running channel) of the moving part, the elastic parameter k of the elastic part, and the working length x of the elastic part. The reset element 941a can also be a wave spring, see [reference needed]. Figure 6 Its working principle is the same as that of the helical spring in the first embodiment, and will not be described again here.

[0039] In some embodiments, limiting members (not shown in the figure) may be provided on both sides of the moving member 942. The limiting members on both sides restrict the movement of the moving member 942 in the movement channel, so that the moving member 942 will not completely detach from the movement channel when it approaches the second end of the movement channel.

[0040] In the third embodiment, the reset member 941b includes a first magnetic member and a second magnetic member. The first magnetic member is located on the wall of the motion channel, specifically on the end face of the first end of the motion channel. The second magnetic member is located on the motion member. The polarity of the opposite sides of the first and second magnetic members is the same. Figure 7 In this embodiment, the opening and closing of the bypass hole can be achieved by designing the pressure-bearing area D of the moving part and the magnetic strength of the magnetic part.

[0041] The motion channel can also be set on the cylinder. Figure 8 This is a schematic diagram of the cylinder structure of the compressor according to the fourth embodiment of the present invention. A motion channel 9c is disposed on the end face of the cylinder 3c. The motion channel 9c includes two sections: one section is arc-shaped, with the center of the arc coinciding with the center of the inner cavity of the cylinder 3c; the other section connects to the arc-shaped section at one end and is open at the other end, passing through the outer wall of the cylinder and connecting to the inner cavity of the compressor housing, thereby achieving communication with the compressor's discharge pressure side. The two ends of the return channel 93c are respectively connected to the other end of the motion channel 9c and the cylinder's intake port. The return channel 93c can also be arc-shaped, coinciding with the center of the inner cavity of the cylinder 3c. A bypass hole 92c can be disposed on the wall surface of the cylinder 3c inside the motion channel 9c, connecting the cylinder's intake chamber and the motion channel 9c. The structure of the moving part 942c is adapted to the arc-shaped moving channel 9c. At this time, the reset part 941c moves back and forth in a pendulum manner. The movement logic of the moving part 942c and the reset part 941c is the same as that of the first to third embodiments.

[0042] Of course, the pump body assembly of the compressor in other embodiments may include two or more cylinders. When the pump body assembly includes at least two cylinders, an upper cylinder head, at least one intermediate plate, and a lower cylinder head, the motion channel is disposed within the upper cylinder head, cylinder, intermediate plate, or lower cylinder head. When the motion channel is disposed within the upper cylinder head, cylinder, or lower cylinder head, the structure of the motion channel can refer to the structure of the first to the lowest four embodiments, and will not be described in detail here.

[0043] Figure 9 This is a schematic diagram of the compressor structure according to the fifth embodiment of the present invention. The pump body assembly includes an upper cylinder head 1d, a lower cylinder head 2d, two cylinders 3d, and an intermediate plate 7. A motion channel 9d is disposed on the intermediate plate 7. The structure of the motion channel 9d can be the same as that of the motion channel 9 in the first embodiment. Two bypass holes 92d respectively connect the motion channel 9d and the working chamber of one cylinder 3d. The return channel includes a first return hole 93d disposed on the intermediate plate 7 and second return holes 931d respectively disposed on the two cylinders 3d. The two ends of the second return hole 931d are respectively connected to the first return hole 93d and the suction port of one cylinder 3d.

[0044] The variable-capacity compressor structure of this invention is adaptive. When the load of the air conditioning system increases and the demand on the compressor's capacity increases, the pressure difference between the compressor's intake and exhaust increases, and the compressor operates at full capacity. Conversely, under low-pressure-difference conditions where the demand on the compressor's capacity decreases, a variable-capacity mode is activated. In this mode, before the compressor piston rotates to the bypass port, the cylinder's intake chamber and intake port are connected, resulting in a reduction in the actual refrigerant drawn into the compressor and a decrease in displacement. Although the system is in a low-demand state at this time, the controller will still control the speed to increase in order to achieve this low-demand state, indirectly achieving a certain high speed for the compressor in the low-demand state and avoiding various problems that occur when the compressor operates at low frequencies.

[0045] When the compressor of this invention is applied to an air conditioning system, the operating condition for initiating capacity change can be determined according to the operating requirements of the air conditioning system. Based on the force balance of the moving parts, by controlling the variable capacity structural parameters D, k, and x, the movement is controlled to be in a second state, i.e., the moving parts avoid the open end of the bypass hole connecting to the moving channel, thus connecting the bypass hole and the moving channel, and the compressor operates in a variable capacity state. Further, if the air conditioning system load increases under this condition, and the demand on the compressor's capacity increases, the compressor speed n increases, the deformation of the reset component increases, the moving parts move towards the low-pressure side, and the moving parts move towards the open end of the bypass hole connecting to the moving channel, gradually closing the connection between the bypass hole and the moving channel. The moving parts are in a first state, and the compressor gradually returns to full capacity operation.

[0046] Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of the present invention.

[0047] The above description, in conjunction with specific preferred embodiments, provides a further detailed explanation of the present invention. It should not be construed that the specific implementation of the present invention is limited to these descriptions. For those skilled in the art, various simple deductions or substitutions can be made without departing from the concept of the present invention, and all such modifications and substitutions should be considered within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that, The compressor's pump body assembly is provided with a variable displacement structure, which includes a bypass hole, a motion channel, and a return channel; The first end of the motion channel is connected to the return channel, and the second end is connected to the exhaust pressure side of the compressor. A reset component and a moving component are provided in the motion channel. The two ends of the reset component abut against the wall of the motion channel and the moving component, respectively. One end of the bypass hole is connected to the motion channel, and the other end is connected to the inner cavity of the cylinder; One end of the return channel is connected to the suction pressure side of the compressor; The moving part is subjected to inhalation pressure and exhaust pressure on both sides respectively. Under the action of the pressure difference on both sides and the reset part, the moving part can reciprocate within the moving channel. The moving part is in the first state, covering the bypass hole, so that the bypass hole is not connected to the return channel; The moving part is in the second state, avoiding the bypass hole, so that the bypass hole is connected to the return channel.

2. The compressor according to claim 1, characterized in that, The reset component is an elastic component, which is one of a spring, rubber, and shape memory alloy components.

3. The compressor according to claim 1, characterized in that, The reset component includes a first magnetic component and a second magnetic component. The first magnetic component is located on the wall of the motion channel, and the second magnetic component is located on the motion component. The polarities of the first magnetic component and the second magnetic component are the same on opposite sides.

4. The compressor according to claim 1, characterized in that, The refrigerant, compressed by the pump assembly, is discharged into the inner cavity of the compressor housing, and the discharge pressure side includes the inner cavity of the housing.

5. The compressor according to claim 4, characterized in that, The second end of the motion channel is an open end.

6. The compressor according to claim 1, characterized in that, The intake pressure side includes a cylinder intake port, a reservoir, or an intake pipe between the reservoir and the cylinder intake port.

7. The compressor according to claim 1, characterized in that, The moving part avoids the bypass hole when it is initially in the moving position, and the bypass hole is connected to the return channel through the moving channel.

8. The compressor according to claim 1, characterized in that, The pressure difference experienced by the moving part when it is at a critical position that is about to close the bypass hole is set as the first pressure difference threshold P1, and the pressure difference experienced by the moving part when it is at a critical position that is about to avoid the bypass hole is set as the second pressure difference threshold P2. When the pressure difference between the compressor's suction pressure Ps and discharge pressure Pd When the pressure difference exceeds the first differential pressure threshold P1, the moving part moves towards the direction of the return channel and gradually covers the bypass hole, causing the bypass hole to disconnect from the moving channel. When the pressure difference between the compressor's suction pressure Ps and discharge pressure Pd When the pressure difference is not greater than the second differential pressure threshold P2, the moving part moves away from the return channel and gradually avoids the bypass hole, so that the bypass hole is connected to the moving channel.

9. The compressor according to claim 1, characterized in that, Limiting members are provided on both sides of the moving part to restrict the movement stroke of the moving part within the movement channel.

10. The compressor according to claim 1, characterized in that, The motion channel is located on the cylinder of the pump body assembly, or on the cylinder cover covering the cylinder end face.

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