Compressor and refrigeration apparatus

Abstract

This invention relates to the field of compressor technology, specifically to a compressor and refrigeration equipment. The compressor includes a cylinder body, a piston assembly, and a switching device. The cylinder body includes a cylinder body and a cylinder head, the cylinder head having a first intake port and a second intake port. The piston assembly includes a piston movably disposed within the cylinder body, the piston having a first dead center near the cylinder head and a second dead center away from the cylinder head during its stroke. The switching device controls the opening and closing of the second intake port. By providing the first and second intake ports on the cylinder head, the first and second intake ports can draw air from different sources, allowing the compressor to sequentially draw air from different sources, reducing the limitation imposed by a single intake port on the compressor's air intake.

Description

Technical Field

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

[0002] The compressor is the core component and energy-intensive part of refrigeration equipment, thus placing higher demands on its refrigeration performance and energy efficiency. Refrigeration equipment requires the compressor to compress the refrigerant during cooling. The compressor typically draws the refrigerant into the cylinder through an intake port, where it is then compressed by the piston. The compressor's intake volume determines the amount of refrigerant it compresses per cycle, which in turn affects the refrigeration efficiency of the equipment. Currently, most compressors only have one intake port, significantly limiting their intake volume. Summary of the Invention

[0003] The main objective of this invention is to propose a compressor that addresses the problem that traditional compressors have only one intake port, which significantly limits the amount of air intake.

[0004] To achieve the above objectives, the present invention provides a compressor comprising:

[0005] The cylinder body includes a cylinder body and a cylinder head disposed at one end of the cylinder body, wherein the cylinder head is provided with a first intake port and a second intake port;

[0006] A piston assembly includes a piston movably disposed within the cylinder body, the piston having a first dead center near the cylinder head and a second dead center away from the cylinder head during its stroke; and...

[0007] A switching device for controlling the opening and closing of the second air intake port.

[0008] Optionally, the distance between the first air intake and the second air intake is greater than 0.5 mm.

[0009] Optionally, the cylinder head is provided with an exhaust chamber on the side facing the cylinder body, the first intake port and the second intake port are located on the outer periphery of the exhaust chamber, and the first intake port and the second intake port are directly connected to the interior of the cylinder body.

[0010] Optionally, the cylinder head has a protrusion on the side away from the cylinder body, facing away from the cylinder body, and the protrusion has a cavity that communicates with the exhaust chamber.

[0011] The first air intake hole and the second air intake hole are respectively misaligned with the protrusion.

[0012] Optionally, the first air intake hole and the second air intake hole are disposed opposite each other on both sides of the protrusion.

[0013] Optionally, the cross-sectional area of ​​the second air intake is s, and 0.1 mm. 2 ≤s≤50mm 2 .

[0014] Optionally, the compressor further includes a switching valve plate disposed on the cylinder head corresponding to the first intake port. The switching valve plate is disposed between the cylinder head and the cylinder body. The switching valve plate has a first through hole relative to the second intake port, so that the second intake port communicates with the inside of the cylinder body through the first through hole.

[0015] Optionally, the switching device is a solenoid valve.

[0016] Optionally, the piston also has an intake position located between the first dead point and the second dead point during its active stroke, and the switching device is used to open the second intake port when the piston is located between the second dead point and the intake position;

[0017] The distance between the inhalation position and the first stop point is L, and the distance between the first stop point and the second stop point is S, wherein 0.5S < L.

[0018] Optionally, the cylinder body extends horizontally, and the second intake port is located in the upper half of the cylinder head.

[0019] The present invention also proposes a refrigeration device, including a compressor, said compressor comprising:

[0020] The cylinder body includes a cylinder body and a cylinder head disposed at one end of the cylinder body, wherein the cylinder head is provided with a first intake port and a second intake port;

[0021] A piston assembly includes a piston movably disposed within the cylinder body, the piston having a first dead center near the cylinder head and a second dead center away from the cylinder head during its stroke; and...

[0022] A switching device for controlling the opening and closing of the second air intake port.

[0023] Optionally, the refrigeration device is a refrigerator.

[0024] Optionally, the intake pressure of the first intake port is P1, and the intake pressure of the second intake port is P2, wherein 1 < P2 / P1 ≤ 6.

[0025] In the technical solution of this invention, by providing a first intake port and a second intake port on the cylinder head, the first intake port and the second intake port can respectively draw air from different air sources, allowing the compressor to sequentially draw air from different air sources, thereby reducing the restriction of the intake port on the compressor's air intake. Since the first intake port and the second intake port draw air from different air sources, their intake pressures may differ during intake, which could lead to interference when they draw air simultaneously. Therefore, the first intake port and the second intake port need to be used alternately. In this solution, when the piston moves from the first dead center towards the second dead center, the first intake port opens to draw air; when the piston moves to near the second dead center, the first intake port closes, and the switching device controls the second intake port to open to draw air. The compressor achieves dual intake by alternately opening the first and second intake ports, thereby reducing the restriction of a single intake port on the compressor and increasing the compressor's air intake volume. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0027] Figure 1 A cross-sectional schematic diagram of an embodiment of the compressor provided by the present invention;

[0028] Figure 2 for Figure 1 A schematic diagram of the middle section structure;

[0029] Figure 3 for Figure 1 Schematic diagram of the middle cylinder head;

[0030] Figure 4 for Figure 3 Top view of the cylinder head;

[0031] Figure 5 for Figure 1 A top view of another embodiment of the cylinder head;

[0032] Figure 6 for Figure 3 Cross-sectional view of the cylinder head.

[0033] Explanation of icon numbers:

[0034] label name label name 100 compressor 1 Cylinder block 11 Cylinder body 12 Cylinder head 121 Second air intake port 122 bump 2 Piston assembly 21 piston 3 Switch valve plate 31 First through hole

[0035] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0036] 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 a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0037] It should be noted that if the embodiments of the present invention involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indicators will also change accordingly.

[0038] Furthermore, if the embodiments of this invention involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Features defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the meaning of "and / or" throughout the text includes three parallel solutions; for example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this invention.

[0039] The compressor is the core component and energy-intensive part of refrigeration equipment, thus placing higher demands on its refrigeration performance and energy efficiency. Refrigeration equipment requires the compressor to compress the refrigerant during cooling. The compressor typically draws the refrigerant into the cylinder through an intake port, where it is then compressed by the piston. The compressor's intake volume determines the amount of refrigerant it compresses per cycle, which in turn affects the refrigeration efficiency of the equipment. Currently, most compressors only have one intake port, significantly limiting their intake volume.

[0040] In view of this, the present invention proposes a compressor that aims to solve the problem that traditional compressors only have one intake port, which greatly limits the intake volume of the compressor. Figures 1 to 6This is an embodiment of the compressor provided by the present invention.

[0041] Please see Figures 1 to 3 The compressor 100 proposed in this invention includes: a cylinder body 1, a piston assembly 2, and a switching device. The cylinder body 1 includes a cylinder body 11 and a cylinder head 12 disposed at one end of the cylinder body 11. The cylinder head 12 is provided with a first intake port and a second intake port 121. The piston assembly 2 includes a piston 21 movably disposed within the cylinder body 11. The piston 21 has a first dead point near the cylinder head 12 and a second dead point away from the cylinder head 12 during its active stroke. The switching device is used to control the opening and closing of the second intake port 121.

[0042] In the technical solution of the present invention, a first intake hole is provided on the cylinder head 12, and a second intake hole 121 is also provided on the cylinder head 12, so that the first intake hole and the second intake hole 121 can respectively enter air from different air sources, so that the compressor 100 can enter air from different air sources in sequence, thereby reducing the restriction of the intake hole on the intake of the compressor 100.

[0043] The air source for the first air intake port may be different from the air source for the second air intake port 121. Therefore, the air intake pressure of the first air intake port and the air intake pressure of the second air intake port 121 may be different. This will cause mutual interference when the first air intake port and the second air intake port 121 are drawing air at the same time. Therefore, the first air intake port and the second air intake port 121 need to be used alternately.

[0044] In this design, when the piston 21 moves from the first stop point toward the second stop point, the first intake port opens to draw in air; when the piston 21 moves to a position near the second stop point, the first intake port closes, and the switching device controls the second intake port 121 to open to draw in air. The compressor 100 achieves dual intake by alternately opening the first intake port and the second intake port 121, thereby reducing the restriction of a single intake port on the compressor 100 and increasing the intake volume of the compressor 100.

[0045] Further, please refer to Figures 3 to 6The cylinder head 12 is provided with a first intake port and a second intake port 121. However, the first intake port needs to be positioned at a certain distance from the second intake port 121; otherwise, the refrigerant in the first intake port may cross-contaminate with the refrigerant in the second intake port, causing their intake to interfere with each other. Therefore, the distance between the first intake port and the second intake port 121 is greater than 0.5 mm. This ensures that the first intake port and the second intake port 121 do not cross-contaminate, allowing for normal air intake from both ports.

[0046] Furthermore, the cylinder head 12 is provided with an exhaust chamber on the side facing the cylinder body 11, and the first intake port and the second intake port 121 are provided on the outer periphery of the exhaust chamber, and the first intake port and the second intake port 121 are directly connected to the interior of the cylinder body 11.

[0047] In this embodiment, when the piston 21 moves toward the cylinder head 12, it compresses the refrigerant in the cylinder block 1. When the piston 21 reaches the first dead center, the gas pressure in the cylinder block 1 is very high. During exhaust, the high-pressure refrigerant in the cylinder block 1 may damage the exhaust structure. Therefore, the cylinder block 1 has an exhaust chamber inside the cylinder head 12, so that the high-pressure refrigerant in the cylinder block 1 has a space to buffer before entering the exhaust port, thus ensuring normal exhaust.

[0048] When the compressor 100 discharges air, the high-pressure refrigerant in the cylinder passes through the discharge chamber. However, if both the first suction port and the second suction port 121 are connected to the discharge chamber, they may be damaged during the compressor's discharge process. Therefore, avoiding the discharge chamber ensures the normal operation of both the first and second suction ports 121. The first suction port and the second suction port 121 are located on the outer periphery of the discharge chamber, thus preventing them from communicating with the discharge chamber.

[0049] Furthermore, the cylinder head 12 has a protrusion 122 on the side away from the cylinder body 11 and facing away from the cylinder body 11. The protrusion 122 has a cavity that communicates with the exhaust chamber. The first intake port and the second intake port 121 are respectively misaligned with the protrusion 122.

[0050] In practical applications, the thickness of the cylinder head 12 may not allow for an exhaust chamber of sufficient size. In this embodiment, the protrusion 122 is provided on the cylinder head 12, and a cavity is added within the protrusion 122. The cavity communicates with the exhaust chamber, thus providing sufficient space to buffer the high-pressure refrigerant in the cylinder block 1.

[0051] Regarding the protrusion 122, it should be noted that the first air intake hole should be offset from the protrusion 122, and the second air intake hole 121 should be offset from the protrusion 122, thus preventing both from communicating with the exhaust chamber. The protrusion 122 can be provided with corresponding clearance portions, such as clearance notches or clearance grooves, to avoid the positions of the first air intake hole and the second air intake hole 121.

[0052] Furthermore, the first air intake hole and the second air intake hole 121 are disposed opposite each other on both sides of the protrusion 122.

[0053] The first intake port is located on the cylinder head 12, and the second intake port 121 is located on the cylinder head 12. However, the two need to be set at a certain distance apart. Otherwise, the first intake port and the second intake port 121 may cross-flow, causing their intake to affect each other.

[0054] In this embodiment, the protrusion 122 separates the first air intake hole and the second air intake hole 121 respectively, thereby ensuring a certain gap so that the first air intake hole and the second air intake hole 121 can intake air normally.

[0055] Furthermore, the cross-sectional area of ​​the second air intake 121 is s, and 0.1 mm. 2 ≤s≤50mm 2 .

[0056] In this embodiment, the second intake port is disposed on the cylinder head 12. Therefore, when the second intake port 121 is too large, it may affect the strength of the cylinder head 12 and the arrangement of other structures on the cylinder head; when the second intake port 121 is too small, the intake volume of the second intake port 121 will be affected, resulting in the compressor 100 having too small an intake volume.

[0057] In practical applications, the cross-sectional area of ​​the second air intake 121 is greater than 50 mm². 2 If the second intake port 121 is too large, it may affect the strength of the cylinder head 12. The cross-sectional area of ​​the second intake port 121 is less than 0.1 mm. 2 At that time, the intake volume is small, which is difficult to meet the intake requirements of the compressor 100.

[0058] The cross-sectional area of ​​the second air intake 121 is less than or equal to 50 mm. 2 And greater than or equal to 0.1mm 2 This is a suitable timeframe. Under these conditions, the air intake volume of the second air intake 121 is considerable, and the size of the second air intake 121 is appropriate. Of course, the size of the second air intake 121 can also be adjusted according to usage requirements.

[0059] Further, please refer to Figure 2 The compressor 100 further includes a switching valve plate 3 disposed on the cylinder head 12 corresponding to the first intake port. The switching valve plate 3 is disposed between the cylinder head 12 and the cylinder body 11. The switching valve plate 3 is provided with a first through hole 31 opposite to the second intake port 121, so that the second intake port 121 communicates with the inside of the cylinder body 11 through the first through hole 31.

[0060] In this embodiment, the cylinder head 12 is provided with the first intake port and may also be provided with an exhaust port. Therefore, a switching valve plate 3 is generally provided between the cylinder head 12 and the cylinder body 11 to control the connection between the first intake port and the exhaust port and the interior of the cylinder body 11. The switching valve plate 3 may block the first intake port, which is also located on the cylinder head 12. Therefore, the switching valve plate 3 is provided with a first through hole 31, so that the second intake port 121 is directly connected to the interior of the cylinder body 11, ensuring the normal use of the second intake port 121.

[0061] The switching device can be implemented in various ways, as long as it can control the opening and closing of the second air intake 121. The present invention does not limit the implementation of the switching device. Specifically, the switching device can be configured as a solenoid valve, or it can be configured as a valve plate; no specific limitation is imposed.

[0062] Taking the compressor 100 used in the refrigeration system of a refrigerator as an example, during the refrigeration process, the high-temperature and high-pressure refrigerant gas is transported from the compressor 100 to the evaporators of the corresponding freezer and refrigerator compartments for evaporation and heat absorption, thereby achieving refrigeration in the freezer and refrigerator compartments. However, the temperatures set in the freezer and refrigerator compartments are not the same, and their evaporation temperatures are different. The temperature and pressure of the refrigerant after heat exchange in the freezer and refrigerator compartments are different. Furthermore, in the prior art, the compressor 100 achieves the refrigeration function of freezing and refrigeration through a single flow path. Thus, whether the freezer or refrigerator compartment needs to be refrigerated, the entire heat exchange system needs to participate in the work, resulting in high energy consumption and low energy efficiency.

[0063] Please see Figure 1The compressor 100 includes a cylinder body 1, a piston assembly 2, and a switching device. The cylinder head 12 is provided with a first intake port and a second intake port 121. The first intake port is used to communicate with a first condensation flow path; the second intake port 121 is used to communicate with a second condensation flow path. The piston assembly 2 includes a piston 21 movably disposed in the cylinder body 1. A working chamber is formed between the piston 21 and the bottom of the cylinder body 1. During its active stroke, the piston 21 has a first dead point located near the bottom of the working chamber and a second dead point located away from the bottom of the working chamber.

[0064] In the technical solution provided by this invention, by setting two parallel flow paths, namely the freezing condensation flow path and the refrigeration condensation flow path, the high-temperature and high-pressure refrigerant formed by the compressor 100 can be reasonably distributed to the freezing flow path and the refrigeration flow path. Because the high-temperature and high-pressure refrigerant formed by the compressor 100 returns to the compressor 100 at a lower temperature and lower pressure after passing through the evaporator corresponding to the freezing compartment, while the high-temperature and high-pressure refrigerant formed by the compressor 100 returns to the compressor 100 at a higher temperature and higher pressure after passing through the evaporator corresponding to the refrigeration compartment. The working chamber of the cylinder 1 is simultaneously connected to both the first suction port and the second suction port 121, allowing refrigerant of relatively low temperature and low pressure returning from the freezer compartment to be transported to the cylinder 1 of the compressor 100 through the first suction port and the second suction port 121 through the first suction channel and the second suction channel, respectively. Conversely, refrigerant of relatively high temperature and high pressure returning from the refrigerator compartment is transported to the compressor 100 through the second suction port 121. When the cylinder 1 compresses the refrigerant gas transported through the first suction port, the second suction port 121 can replenish the working chamber, thereby increasing the suction volume of the working chamber of the cylinder 1 and improving the compression efficiency of the compressor 100. Furthermore, by using two parallel flow paths to achieve their respective operating conditions, power consumption is reduced. Since the compressor 100 of this invention is equipped with a second suction port 121, the embodiments of the refrigeration equipment of this invention include all the technical solutions of all the embodiments of the second suction port 121 described above, and the achieved technical effects are completely the same, and will not be repeated here.

[0065] The first and second intake ports 121 have different intake pressures, therefore they intake sequentially. The first intake port has a lower intake pressure and therefore intakes first. When the compressor 100 is intakeing air, the air pressure inside the cylinder 1 gradually increases, causing the intake speed of the first intake port to slow down or even fail to intake properly. Therefore, in one embodiment of the present invention, please refer to... Figure 1The piston 21 also has an intake position located between the first stop point and the second stop point during its active stroke. The switching device is used to open the second intake port 121 when the piston 21 is located between the second stop point and the intake position. The distance between the intake position and the first stop point is L, and the distance between the first stop point and the second stop point is S, where 0.5S < L.

[0066] When the piston 21 moves toward the second dead center, air is introduced through the first intake port. Before reaching the intake position, air is introduced through the first intake port. When the piston 21 moves to the intake position, the air pressure inside the cylinder 1 increases. The lower intake pressure of the first intake port results in a lower intake rate. Therefore, the compressor 100 closes the first intake port and opens the second intake port 121 via the switching device when the piston 21 is in the intake position. The intake pressure of the second intake port 121 is higher, allowing for continued air intake. During the movement of the piston 21, the opening and closing states of the first intake port and the second intake port 121 are as follows:

[0067] The intake stroke of a cylinder includes:

[0068] First stroke: The piston 21 moves from the first dead center to the second dead center, and is located between the intake position and the first dead center. During the first stroke, the control valve group is open, making the first intake port open, and the second intake port 121 is closed by the switching device. At this time, the working chamber of the cylinder 1 only draws air through the first intake port. At this time, the total amount of refrigerant in the working chamber comes from the first intake port, that is, the refrigerant in the first condensation circuit. It can be understood that as the piston 21 moves towards the position closer to the second dead center, the compression space of the working chamber of the cylinder 1 increases, and it is in a negative pressure state, which facilitates the external airflow to enter the working chamber of the cylinder 1 from the first intake port. However, since the airflow pressure through the first intake port is less than the airflow pressure through the second intake port 121, during this stroke, the switching device blocks the second intake port 121 to prevent the airflow from the second intake port 121 from obstructing the airflow from the first intake port into the working chamber of the cylinder 1.

[0069] Second stroke: The piston 21 moves from the first dead center to the second dead center, and is located between the intake position and the second dead center. During the second stroke, the switching device opens the second intake port 121, so that the second intake port 121 connects to the working chamber of the cylinder 1. At this time, the control valve group switches between the open and closed states as needed. When the control valve group is in the open state, the first intake port and the second intake port 121 simultaneously input airflow into the working chamber of the cylinder 1. Since a certain amount of airflow is drawn into the space of the working chamber of the cylinder 1 through the first intake port during the first stroke, there is a certain airflow pressure in the compression space. Therefore, when airflow is input into the working chamber of the cylinder 1 through the second intake port 121, the impact on the airflow of the first intake port is small. When the control valve group is in the closed state, the second intake port 121 inputs airflow into the working chamber of the cylinder 1. At this time, the refrigerant replenished into the working chamber comes from the second intake port 121, that is, the refrigerant of the second condensation circuit flows back into the working chamber of the cylinder 1. Understandably, the closer the second suction port 121 is to the midpoint between the first and second stop points, the earlier it opens and the later it closes, resulting in a longer supply time of high-pressure refrigerant from the second condensing circuit and a larger gas replenishment volume. Conversely, the closer the second suction port 121 is to the second stop point, the later it opens and the earlier it closes, resulting in a shorter supply time of high-pressure refrigerant from the second condensing circuit and a shorter gas replenishment time, thus reducing the gas replenishment volume. In practice, the position of the second suction port 121 can be set according to the required gas replenishment volume.

[0070] The compression stroke of a cylinder includes:

[0071] Third stroke: The piston 21 moves from the second dead center towards the first dead center, and is located between the second dead center and the intake position. During the third stroke, the control valve assembly is closed, and the piston 21 moves rapidly towards the first dead center. At this time, the second intake port 121 still supplies airflow into the working chamber of the cylinder 1. The refrigerant supplied to the working chamber at this time comes from the second intake port 121. Therefore, during the third stroke, when the airflow in the working chamber of the cylinder 1 is compressed, it does not excessively obstruct the airflow input into the working chamber of the cylinder 1 through the second intake port 121, allowing the cylinder 1 to still draw in airflow during the compression stroke. Furthermore, since the working chamber of the cylinder 1 contains a mixture of airflow from the first intake port and the second intake port 121, the airflow pressure in the working chamber of the cylinder 1 is lower than the airflow pressure through the second intake port 121.

[0072] Fourth stroke: The piston 21 moves from the second dead center towards the first dead center, and is positioned between the first dead center and the intake position. During the fourth stroke, the control valve assembly remains closed, and the switching device closes the second intake port 121. During this process, the piston 21 compresses the airflow in the working chamber of the cylinder 1 into a high-pressure airflow. When the piston 21 reaches the second dead center, the airflow pressure in the working chamber of the cylinder 1 is fully compressed. At this time, the control valve assembly connecting the output pipe of the working chamber of the cylinder 1 switches from the closed state to the open state to output the compressed high-pressure airflow.

[0073] The corresponding working circuits for the two condensation flow paths are as follows:

[0074] The airflow path in the first intake airflow channel is: the first condensation airflow channel → the first intake port → the working chamber of the cylinder 1.

[0075] The airflow path in the second intake airflow channel is: the second condensation airflow path → the second intake port 121 → the working chamber of the cylinder 1.

[0076] Furthermore, the compressor 100 also includes an inner exhaust pipe that communicates with the working chamber of the cylinder 1. The inner exhaust pipe is used to communicate with the outer exhaust pipe so that the compressed high-pressure airflow in the working chamber of the cylinder 1 is discharged from the inner exhaust pipe to the outer exhaust pipe.

[0077] In practical terms, the first condensing flow path corresponds to the freezer compartment of the refrigerator. Because the freezer compartment requires a larger cooling capacity, it requires a larger amount of refrigerant, and during operation, the pressure of the refrigerant consumed is also higher. The second condensing flow path corresponds to the refrigerator compartment, which requires a smaller cooling capacity, and therefore consumes less refrigerant. Thus, the pressure returning to the first suction port is much lower than the pressure at the second suction port 121. However, the amount of refrigerant in the first condensing flow path is larger. Therefore, when the compressor 100 is working, the piston 21 primarily opens the first suction port during the first half of the suction stroke to perform main suction, drawing in a larger amount of refrigerant from the condensing flow path corresponding to the freezer compartment. In the latter half of the suction stroke… During the process, the second suction port 121 is connected to the working chamber, the first suction port is closed, and the second suction port 121 begins to be supplied with high-pressure refrigerant gas. Gas supply continues during the first small portion of the compression stroke, and finally, during the latter large portion of the compression stroke, the second suction port 121 closes. The piston 21 compresses the refrigerant in the working chamber. By setting the relative distance between the suction position and the first and second dead points using the switching device, the intake volume of the second suction port 121 can be controlled. That is, due to the setting of the suction position, the opening and closing duration of the second suction port 121 can be adjusted during the reciprocating motion of the piston 21, thereby adjusting the flow rate ratio between the first and second suction ports 121.

[0078] It should be noted that the distance between the first stop point and the second stop point is S. That is, the first stop point refers to the position of the end face of the piston 21 closest to the bottom of the working chamber when it has moved to its closest distance to the bottom wall of the cylinder 1. The second stop point refers to the position of the end face of the piston 21 closest to the bottom wall of the cylinder 1 when it has moved to its farthest distance from the bottom of the working chamber. In other words, distance S is the distance between the two extreme states of the end face of the piston 21 closest to the bottom wall of the cylinder 1. The distance between the intake position and the first stop point is L, that is, the distance between the centerline of the second intake port 121 and the first stop point is L.

[0079] Furthermore, during use, engine oil is applied to the piston 21 and the side wall of the cylinder body 1, which may deposit on the lower half of the cylinder body 1. If the second intake port 121 is located on the lower half of the side wall of the cylinder body 1, it may be affected by oil seepage, impacting its normal operation. Therefore, in one embodiment, the cylinder body 1 extends horizontally, and the second intake port 121 is located on the upper half of the cylinder head 12.

[0080] The present invention also proposes a refrigeration device, including the compressor 100 as described above. The refrigeration device uses refrigerant compressed by the compressor 100 to perform refrigeration, thereby achieving high refrigeration efficiency.

[0081] Furthermore, the refrigeration device is a refrigerator. The refrigerator itself has multiple different air sources, such as a refrigeration evaporator and a freezing evaporator, which can fully utilize the dual-suction function of the compressor 100. Of course, the refrigeration device can also be an air conditioner, and is not limited to a refrigerator.

[0082] Furthermore, the intake pressure of the first intake port is P1, and the intake pressure of the second intake port 121 is P2, wherein 1 < P2 / P1 ≤ 6.

[0083] When the intake pressure of the first intake port and the second intake port 121 are the same, it becomes difficult for the first intake port and the second intake port 121 to draw in air when the air pressure inside the cylinder 1 rises. Furthermore, during the intake process, the intake speed of the compressor 100 decreases as the pressure difference decreases, thus affecting the intake volume of the compressor 100.

[0084] Therefore, in this embodiment, the intake pressure of the second intake port 121 is different from that of the first intake port. The air pressure in the working chamber is low when the intake begins. By opening the first intake port, air is drawn from the air source with relatively low air pressure. After a period of time, the air pressure in the cylinder 1 rises, and the intake efficiency of the first intake port also weakens. At this time, the second intake port 121 is opened to continue to draw air from the air source with relatively high air pressure. At this time, the intake rate is still relatively fast, thereby increasing the intake volume of the compressor 100 and improving the refrigeration efficiency of the refrigeration equipment.

[0085] The above description is merely an optional embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made under the concept of the present invention using the description and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A compressor, characterized in that, include: The cylinder body includes a cylinder body and a cylinder head disposed at one end of the cylinder body, wherein the cylinder head is provided with a first intake port and a second intake port; A piston assembly includes a piston movably disposed within the cylinder body, the piston having a first dead center near the cylinder head and a second dead center away from the cylinder head during its active stroke; The control valve assembly controls the opening and closing of the first intake port; as well as, A switching device for controlling the opening and closing of the second air intake port; The first air intake is used to connect to the freezing condensation flow path, and the second air intake is used to connect to the refrigeration condensation flow path; The airflow pressure at the first intake port is less than the airflow pressure through the second intake port; The cylinder head has an exhaust chamber on the side facing the cylinder body. The first intake port and the second intake port are located on the outer periphery of the exhaust chamber, and the second intake port is directly connected to the interior of the cylinder body. The cylinder head has a protrusion on the side away from the cylinder body, facing away from the cylinder body. The protrusion has a cavity that communicates with the exhaust chamber. The second intake port is misaligned with the protrusion. The first air intake hole and the second air intake hole are disposed opposite each other on both sides of the protrusion; The piston also has an intake position located between the first dead point and the second dead point during its active stroke. The intake stroke of the piston includes: First stroke: The piston moves from the first dead point to the second dead point and is located between the intake position and the first dead point. During the first stroke, the control valve group is opened, so that the first intake port is open and the second intake port is closed by the switch device. Second stroke: The piston moves from the first dead point to the second dead point and is located between the intake position and the second dead point. During the second stroke, the switching device opens the second intake port, so that the second intake port is connected to the working chamber of the cylinder. At this time, the control valve group is in the open or closed state. The cross-sectional area of ​​the second air intake is s, and 0.1 mm. 2 ≤s≤50mm 2 ; The distance between the inhalation position and the first stop point is L, and the distance between the first stop point and the second stop point is S, wherein 0.5S < L.

2. The compressor as described in claim 1, characterized in that, The distance between the first air intake hole and the second air intake hole is greater than 0.5 mm.

3. The compressor as described in claim 1, characterized in that, The compressor further includes a switching valve plate disposed on the cylinder head corresponding to the first intake port. The switching valve plate is disposed between the cylinder head and the cylinder body. The switching valve plate has a first through hole relative to the second intake port, so that the second intake port communicates with the inside of the cylinder body through the first through hole.

4. The compressor as described in claim 1, characterized in that, The cylinder body extends horizontally, and the second intake port is located on the upper half of the cylinder head.

5. A refrigeration device, characterized in that, Includes the compressor as described in any one of claims 1 to 4.

6. The refrigeration equipment as described in claim 5, characterized in that, The intake pressure of the first intake port is P1, and the intake pressure of the second intake port is P2, wherein 1 < P2 / P1 ≤ 6.

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