Compressors and refrigeration equipment

Abstract

The present application discloses a compressor and a cooling device, the compressor includes a cylinder body and a piston component, a first intake hole is provided on a cylinder cover of the cylinder body, the piston has a top dead center close to the cylinder cover of the cylinder body and a bottom dead center far from the cylinder cover of the cylinder body in a moving stroke, the distance between the top dead center and the bottom dead center is S, a second intake hole is provided on the cylinder body or the piston, the second intake hole is provided to communicate with a working chamber when the piston moves to a set position, in the set position, the distance between the piston and the top dead center is L1, and L1>0.5S.

Description

[Technical field]

[0001] This application claims priority to a Chinese patent application with application number 202210155326.6, filed on February 18, 2022, the entire contents of which are incorporated herein by reference.

[0002] The present application relates to the technical field of compressors, and in particular to compressors and refrigeration equipment. [Background technology]

[0003] As the most core component of the refrigeration system and the component with the largest energy consumption, the compressor has higher requirements for its cooling performance and energy efficiency. A household refrigerator generally has a freezer and a refrigerator, and in the process of cooling the freezer and the refrigerator, the evaporation temperatures of the corresponding refrigerants are different, and the pressures of the corresponding refrigerants are also different.

[0004] Unlike the conventional compressor, which uses a single intake pipe line in series to achieve the cooling functions of freezing and refrigeration, the new single-cylinder double independent intake pump body structure has the ability to greatly improve the overall performance of the reciprocating compressor, and in order to obtain a good energy efficiency ratio, the conventional compressor uses a single intake and exhaust compression pump body mechanism basis to achieve a low COP (energy efficiency ratio). During the operation of the compressor, in order to improve its cooling amount and energy efficiency ratio COP, a second intake port is added accordingly. However, due to the difference in the cooling demands of the freezer and the refrigerator during the operation of the compressor cylinder, the refrigerant demands of the freezer and the refrigerator are different. Summary of the Invention [Problem to be solved by the invention]

[0005] The main object of the present application is to provide a compressor and a cooling device, and an object of the present application is to provide a compressor that can rationally allocate the main intake amount and the gas make-up amount while realizing dual intake. [Means for solving the problem]

[0006] In order to achieve the above object, the present application provides a compressor, comprising: a cylinder body, a cylinder cover of the cylinder body is provided with a first intake hole for communicating with a first cooling channel; and a piston component, the piston being movably installed in the cylinder body, a working chamber is formed between the piston and a bottom of the cylinder body, the piston has a top dead center located at the cylinder cover of the cylinder body and a bottom dead center far from the cylinder cover of the cylinder body in a moving stroke, a distance between the top dead center and the bottom dead center is S, the cylinder body or the piston is provided with a second intake hole for communicating with a second cooling channel, the second intake hole is installed to communicate with the working chamber when the piston moves to a set position, and at the set position, a distance between the piston and the top dead center is L1, and L1>0.5S.

[0007] In one embodiment, a second intake hole is formed through the side wall of the cylinder body, and the distance between the second intake hole and the top dead center is L2, and L2>0.5S.

[0008] In one embodiment, when the piston is at the top dead center, a side wall of the piston covers and seals the second intake port.

[0009] In one embodiment, the second air intake hole is a round hole.

[0010] In one embodiment, the hole diameter of the second intake hole is D1, where D1≦6 mm.

[0011] In one embodiment, the compressor further includes a first intake pipe for communicating the first cooling passage and the first intake hole, and a second intake pipe for communicating the second cooling passage and the second intake hole.

[0012] In one embodiment, the inner diameter of the second intake pipe is d1, the outer diameter of the second intake pipe is d2, 0.3 mm≦d1≦6 mm, and 0.4 mm≦d2≦12.5 mm.

[0013] The present application further provides a cooling device, the cooling device including the compressor as described above, the compressor including: a cylinder body, a cylinder cover of the cylinder body is provided with a first intake hole for communicating with a first cooling channel; and a piston component, the piston being movably installed in the cylinder body, a working chamber is formed between the piston and a bottom of the cylinder body, the piston has a top dead center close to the cylinder cover of the cylinder body and a bottom dead center far from the cylinder cover of the cylinder body in a moving stroke, a distance between the top dead center and the bottom dead center is S, the cylinder body or the piston is provided with a second intake hole for being installed to communicate with a second cooling channel, the second intake hole is installed to communicate with the working chamber when the piston moves to a set position, and at the set position, a distance between the piston and the top dead center is L1, and L1>0.5S.

[0014] In one embodiment, the cooling appliance is a refrigerator.

[0015] In one embodiment, the supply pressure of the first intake hole is P1, the supply pressure of the second intake hole is P2, and <P2 / P1≦6である。 Effect of the Invention

[0016] In the technical solution provided in the present application, the compressor includes a cylinder body and a piston component, a cylinder cover of the cylinder body is provided with a first intake hole for communicating with a first cooling channel, the piston component includes a piston movably installed in the cylinder body, a working chamber is formed between the piston and a bottom of the cylinder body, the piston has a top dead center close to the cylinder cover of the cylinder body and a bottom dead center far from the cylinder cover of the cylinder body in a moving stroke, a distance between the top dead center and the bottom dead center is S, a second intake hole is installed in the cylinder body or the piston to be installed to communicate with a second cooling channel, so that the second intake hole is installed to communicate with the working chamber when the piston moves to a set position, and in the set position, a distance between the piston and the top dead center is L1, and L1>0.5S. The first cooling flow path corresponds to the freezer compartment of the refrigerator, and since the amount of cooling required for the freezer compartment is large, the amount of refrigerant required is large and the pressure of the refrigerant consumed during operation is also large. On the other hand, the second cooling flow path corresponds to the refrigerator compartment of the refrigerator, and since the amount of cooling required for the refrigerator compartment is small, the pressure of the refrigerant consumed is also small. In this way, the pressure of the refrigerant returning to the first intake hole is much smaller than the pressure of the second intake hole, but the amount of refrigerant in the first cooling flow path is large. Thus, during the operation of the compressor, the piston first mainly opens the first intake port to perform main intake during the first half of the intake stroke, so as to suck in a large amount of refrigerant in the cooling passage corresponding to the freezing chamber; during the latter half of the intake stroke, the second intake port communicates with the working chamber, the first intake port is closed, and the second intake port starts to supply high-pressure refrigerant gas, and continues to supply gas during the first half of the compression phase; and finally, during the latter half of the compression stroke, the second intake port is closed, and the piston compresses the refrigerant in the working chamber, which not only effectively improves the cooling capacity and energy efficiency ratio of the compressor, but also allows the refrigerant gases of different pressures in the two cooling passages to be reasonably distributed and returned to the compressor.This provides a compressor that can rationally allocate the main intake amount and the gas supply amount while realizing dual intake. [Brief description of the drawings]

[0017] In order to more clearly describe the embodiments of the present application or the technical solutions in the prior art, the following briefly introduces the accompanying drawings that need to be used in the description of the embodiments or the prior art. However, the accompanying drawings in the following description are only some of the embodiments of the present application, and it is obvious to those skilled in the art that they can obtain other accompanying drawings based on the structures shown in these accompanying drawings without paying creative labor. [Figure 1] FIG. 2 is a schematic diagram of the internal structure of one embodiment of a compressor provided in the present application. [Diagram 2] 1 is a schematic cross-sectional view of one embodiment of a compressor provided herein; [Diagram 3] FIG. 2 is a schematic perspective view of the compressor of FIG. 1.

[0018] The realization of the objectives, functional features and advantages of the present application will be further explained in connection with the embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0019] The following clearly and completely describes the technical solutions in the embodiments of the present application with reference to the drawings in the embodiments of the present application, but it is clear that the described embodiments are only some of the embodiments of the present application, and are not all of the embodiments. Based on the embodiments of the present application, other embodiments obtained by those skilled in the art without performing creative labor all fall within the scope of protection of the present application.

[0020] In addition, when directional indications (e.g., up, down, left, right, front, back, etc.) are mentioned in the embodiments of the present application, the directional indications are used only to explain the relative positional relationships, movement conditions, etc. between each component in a certain posture (as shown in the figure), and when the certain posture changes, the directional indications also change accordingly.

[0021] In addition, when the embodiments of the present application refer to "first", "second", etc., the descriptions "first", "second", etc. are used for explanatory purposes only and are not understood to indicate or imply the relative importance or the number of technical features shown. Thus, features defined as "first" and "second" may include at least one of the features explicitly or implicitly. In addition, the meaning of "and / or" throughout this specification includes three parallel schemes, and for example, "A and / or B" includes scheme A, scheme B, or a scheme that satisfies both A and B. In addition, the technical solutions between the embodiments may be combined with each other, but this should be based on what a person skilled in the art can achieve. If the combination of technical solutions is inconsistent or cannot be achieved, it should be considered that such combination of technical solutions does not exist and is not within the scope of protection required by this application.

[0022] As the most core component of the refrigeration system and the component with the largest energy consumption, the requirements for its cooling performance and energy efficiency level are also higher. A household refrigerator generally has a freezer and a refrigerator. In the process of realizing the cooling of the freezer and the refrigerator, the evaporation temperature of the corresponding refrigerant is different, and the pressure of the corresponding refrigerant is also different. The conventional compressor realizes the cooling function of freezing and refrigeration through a single suction pipe in series form, so as to reduce the COP (energy efficiency ratio) of the refrigerator and obtain a good energy efficiency ratio. Unlike the conventional single-suction and exhaust compression pump body structure, the new single-cylinder double independent suction pump body structure has the ability to greatly improve the overall performance of the reciprocating compressor. During the operation of the compressor, in order to improve its cooling amount and energy efficiency ratio COP, a second suction port is added accordingly. However, due to the difference in the cooling demand corresponding to the freezer and the refrigerator during the operation of the compressor cylinder, the refrigerant demand required for the freezer and the refrigerator is different.

[0023] In order to solve the above problems, the present application provides a compressor 100, and FIGS. 1 to 3 show a specific embodiment of the compressor 100 provided in the present application.

[0024] Taking the compressor 100 as an example for use in the cooling system of a refrigerator, in the cooling process of a refrigerator, high-temperature and high-pressure refrigerant gas is transported from the compressor to the evaporators of the corresponding freezing and refrigerating compartments to absorb heat by evaporation, thereby cooling the freezing and refrigerating compartments. However, the set temperatures of the freezing and refrigerating compartments are different, and the evaporation temperatures of the two compartments are different, so that the temperature and pressure of the refrigerant after heat exchange in the freezing and refrigerating compartments are different. Moreover, in the conventional technology, the compressor achieves the cooling functions of freezing and refrigeration through one flow path. Thus, whether it is necessary to cool the freezing or refrigerating compartment, the entire heat exchange system must be involved in operation, resulting in high energy consumption and low energy efficiency ratio.

[0025] 1 to 3, the compressor 100 includes a cylinder body 1 and a piston component 2, a cylinder cover of the cylinder body 1 is provided with a first intake hole 11 for communicating with a first cooling flow path, the piston component 2 includes a piston 21 movably installed in the cylinder body 1, a working chamber 1a is formed between the piston 21 and a bottom of the cylinder body 1, the piston 21 has a top dead center located at the cylinder cover of the cylinder body 1 and a bottom dead center far from the cylinder cover of the cylinder body 1 in a movable stroke, the distance between the top dead center and the bottom dead center is S, the cylinder body 1 or the piston 21 is provided with a second intake hole 12 for being installed to communicate with a second cooling flow path, the second intake hole 12 is installed to communicate with the working chamber 1a when the piston 21 moves to a set position, and at the set position, the distance between the piston 21 and the top dead center is L1, and L1>0.5S.

[0026] In the technical solution provided in the present application, a compressor 100 includes a cylinder body 1 and a piston component 2, a cylinder cover of the cylinder body 1 is provided with a first intake hole 11 for communicating with a first cooling channel, the piston component 2 includes a piston 21 movably installed in the cylinder body 1, the piston 21 has a top dead center close to the cylinder cover of the cylinder body 1 and a bottom dead center far from the cylinder cover of the cylinder body 1 in a moving stroke, a distance between the top dead center and the bottom dead center is S, the cylinder body 1 or the piston 21 is provided with a second intake hole 12 for being installed to communicate with a second cooling channel, the second intake hole 12 is installed to be communicated with the working chamber 1a when the piston 21 moves to a set position, and in the set position, a distance between the piston 21 and the top dead center is L1, and L1>0.5S.The first cooling flow passage corresponds to the freezer compartment of the refrigerator, and the amount of cooling required for the freezer compartment is large, so the amount of refrigerant required is large and the pressure of the refrigerant consumed during the operation is also large. On the other hand, the second cooling flow passage corresponds to the refrigerator compartment of the refrigerator, and the amount of cooling required for the refrigerator compartment is small, so the pressure of the refrigerant consumed is also small. Thus, the pressure of the refrigerant returning to the first intake port 11 is much smaller than the pressure of the second intake port 12, but the amount of refrigerant in the first cooling flow passage is large. Thus, during the operation of the compressor 100, the piston 21 first opens the first intake port 11 mainly to perform main intake during the first half or so of the intake stroke, so that a large amount of refrigerant can be sucked into the cooling flow passage corresponding to the freezer compartment. During the latter half or so of the intake stroke, the second intake port 11 opens the first intake port 12 mainly to perform main intake. The intake hole 12 communicates with the working chamber 1a, the first intake hole 11 closes, the second intake hole 12 starts to supply high-pressure refrigerant gas, and continues to supply gas in a little less than half of the first stroke of the compression stage, and finally, in a little more than half of the last stroke of the compression stage, the second intake hole 12 closes, and the piston 21 compresses the refrigerant in the working chamber 1a. By rationally setting the opening and closing times of the first intake hole 11 and the second intake hole 12, not only can the energy efficiency ratio of the cooling amount of the compressor 100 be effectively improved, but also the refrigerant gases of different pressures in the two cooling passages can be rationally distributed and returned to the compressor 100, thereby providing a compressor 100 that can rationally distribute the main suction amount and the gas supply amount while realizing dual intake.

[0027] 3, the distance between the piston 21 and the top dead center is L1, that is, the distance between the end face of the one end of the piston 21 close to the bottom wall of the cylinder body 1 and the bottom wall of the cylinder body 1 is L1. The distance between the top dead center and the bottom dead center is S, that is, the top dead center is the position where the one end of the piston 21 close to the bottom wall of the cylinder body 1 is located when the end face of the one end of the piston 21 close to the bottom wall of the cylinder body 1 moves to the closest distance to the bottom wall of the cylinder body 1, and the bottom dead center is the position where the one end of the piston 21 close to the bottom wall of the cylinder body 1 is located when the end face of the one end of the piston 21 close to the bottom wall of the cylinder body 1 moves to the farthest distance from the bottom wall of the cylinder body 1. In other words, the distance S is the distance between two extreme states of the end face of the one end of the piston 21 close to the bottom wall of the cylinder body 1.

[0028] As can be understood, the second intake hole 12 may be installed on the bottom wall of the cylinder body 1 and opened and closed by a valve. When the piston 21 moves to the set position, i.e., when the distance from the top dead center is greater than 0.5S, the valve opens, the second intake hole 12 opens to supply gas to the working chamber 1a, and the first intake hole 11 closes. Of course, the second intake hole 12 may be installed on the piston 21 and the valve controls the opening and closing of the second intake hole 12 on the piston 21. Alternatively, the second intake hole 12 is installed on the side wall of the piston 21, and a groove is installed on the side wall of the cylinder body 1 corresponding to the second intake hole 12. By setting the position of the groove, when the piston 21 moves to the set position, the second intake hole 12 corresponds to the groove, and the second intake hole 12 communicates with the working chamber 1a through the groove to supply gas. According to each of the above embodiments, when the piston 21 opens the second intake hole 12 during the latter half of the intake stroke and the first half of the compression stroke, the time during which the first intake hole 11 is open, i.e., the intake time, becomes longer and the amount of intake air of the first intake hole 11 also becomes larger, but the time during which the second intake hole 12 is open is short and the gas supply time is short, and accordingly the amount of gas supply of the second intake hole 12 becomes smaller accordingly, thereby achieving a rational distribution of the amount of refrigerant in the two cooling flow paths.

[0029] Specifically, in this embodiment, a second intake hole 12 is formed through the side wall of the cylinder body 1, the distance between the second intake hole 12 and the top dead center is L2, and L2>0.5S. The first intake hole 11 is provided with a group of control valves for opening and closing it. During the movement of the piston 21, the opening and closing states of the first intake hole 11 and the second intake hole 12 are as follows:

[0030] The intake stroke of a cylinder includes the following: In the first stroke, the piston 21 moves from the top dead center toward the bottom dead center, and the distance from the top dead center is less than 0.5S. In the first stroke, the control valve group opens, the first intake hole 11 is connected, and the second intake hole 12 is blocked by the piston 21. At this time, the working chamber 1a of the cylinder body 1 realizes intake only through the first intake hole 11. At this time, the total amount of refrigerant in the working chamber 1a is the refrigerant from the first intake hole 11, i.e., the first cooling passage. As can be understood, when the piston 21 moves toward a position close to the bottom dead center, the compression space of the working chamber 1a of the cylinder body 1 increases and becomes a negative pressure state, so that the external air flow easily flows into the working chamber 1a of the cylinder body 1 from the first intake hole 11. Meanwhile, the air flow pressure through the first intake hole 11 is smaller than the air flow pressure through the second intake hole 12. Therefore, during this movement stroke, the piston 21 blocks the second intake hole 12, thereby preventing the airflow from the second intake hole 12 from impeding the airflow from the first intake hole 11 from entering the working chamber 1a of the cylinder body 1. In the second stroke, the piston 21 moves from the first dead center toward the second dead center, and the distance from the first dead center is greater than 0.5S. In the second stroke, the piston 21 does not block the second intake hole 12, and the second intake hole 12 communicates with the working chamber 1a of the cylinder body 1. At this time, the control valve group switches between an open state and a closed state according to actual requirements. When the control valve group is in an open state, the first intake hole 11 and the second intake hole 12 simultaneously input airflow into the working chamber 1a of the cylinder body 1. In the first stroke, a certain amount of airflow is sucked into the space of the working chamber 1a of the cylinder body 1 through the first intake hole 11, so that there is a certain airflow pressure in the compression space. Therefore, when the airflow is input into the working chamber 1a of the cylinder body 1 through the second intake hole 12, the influence of the airflow on the first intake hole 11 is small. And the distance from the second intake port 12 to the first dead center is greater than 0.5S, that is, the distance to the first intake port 11 is greater than 0.5S, so there is a suitable buffer distance between them, which reduces the obstruction effect of the airflow of the second intake port 12 on the airflow of the first intake port 11, and improves the compression energy efficiency. When the control valve group is in a closed state, the second intake port 12 inputs the airflow into the working chamber 1a of the cylinder body 1. At this time, the refrigerant replenished in the working chamber 1a is from the second intake port 12, that is, the refrigerant in the second cooling channel all flows back into the working chamber 1a of the cylinder body 1. As can be understood, the closer the second intake hole 12 is to the midpoint between the first dead point and the second dead point, the earlier the opening time of the second intake hole 12 is, the later the closing time is, the longer the time of the high pressure refrigerant supplied from the second cooling passage is, and the larger the amount of gas replenishment is; the closer the second intake hole 12 is to the second dead point, the later the opening time of the second intake hole 12 is, the earlier the closing time is, the shorter the time of the high pressure refrigerant supplied from the second cooling passage is, and the shorter the gas replenishment time is, and therefore the smaller the amount of gas replenishment is. In reality, the position of the second intake hole 12 may be set according to the demand for the amount of gas replenishment.

[0031] The compression stroke of a cylinder includes: In the third stroke, the piston 21 moves from the bottom dead center toward the top dead center, and the distance from the top dead center is greater than 0.5S. In the third stroke, the control valve group closes, and the piston 21 moves rapidly toward the top dead center. At this time, the second intake hole 12 still inputs airflow into the working chamber 1a of the cylinder body 1. At this time, the refrigerant replenished in the working chamber 1a is from the second intake hole 12. Therefore, in the third stroke, when the airflow in the working chamber 1a of the cylinder body 1 is compressed, the airflow input into the working chamber 1a of the cylinder body 1 through the second intake hole 12 is not excessively obstructed, and the cylinder body 1 can suck in the airflow even in the compression stroke. Since the airflows from the first intake port 11 and the second intake port 12 are mixed in the working chamber 1a of the cylinder body 1, the airflow pressure in the working chamber 1a of the cylinder body 1 becomes smaller than the airflow pressure passing through the second intake port 12. In the fourth stroke, the piston 21 moves from the bottom dead center toward the top dead center, and the distance from the top dead center is less than 0.5S. In the fourth stroke, the control valves remain closed, and the piston 21 blocks the second intake port 12. In this process, the piston 21 compresses the airflow in the working chamber 1a of the cylinder body 1 into a high-pressure airflow. When the piston 21 moves to the bottom dead center, the airflow pressure in the working chamber 1a of the cylinder body 1 is compressed to a desired level. At this time, the control valves of the output piping communicating with the working chamber 1a of the cylinder body 1 are switched from a closed state to an open state, and the compressed high-pressure airflow is output.

[0032] In the technical solution of this embodiment, by locating the second intake hole 12 close to the bottom dead center, the compressor 100 does not need to install a special control valve group to control the opening and closing of the second intake hole 12, and the second intake hole 12 can be automatically opened and closed during the moving stroke of the piston 21, which is ingenious in structure and saves costs. Furthermore, by setting the distance of the second intake hole 12 from the top dead center and the bottom dead center, the amount of air supplied to the second intake hole 12 can be controlled; that is, by setting the position of the second intake hole 12, the opening and closing time of the second intake hole 12 can be adjusted when the piston 21 reciprocates, thereby realizing the adjustment of the flow distribution between the first intake hole 11 and the second intake hole 12.

[0033] The operation process of the two corresponding cooling passages of the compressor 100 is as follows. The air flow path in the first intake flow path is from the first external intake pipe to the first intake port 11 and then to the working chamber 1 a of the cylinder body 1 . The air flow path in the second intake flow path is from the second external intake pipe to the second intake port 12 and then to the working chamber 1 a of the cylinder body 1 . The compressor 100 further includes an internal exhaust pipe communicating with the working chamber 1a of the cylinder body 1, and the internal exhaust pipe communicates with an exhaust outer pipe 6 and is used to discharge the high-pressure air flow compressed in the working chamber 1a of the cylinder body 1 from the internal exhaust pipe to the exhaust outer pipe 6.

[0034] The distance between the second intake port 12 and the top dead center is L2, that is, the distance between the center line of the second intake port 12 and the top dead center is L2.

[0035] Furthermore, in order to fully utilize the piston 21 as a valve opening and closing function, and to enable the piston 21 to close the second intake hole 12 during the intake and compression strokes and to keep the second intake hole 12 closed during the first stroke and the fourth stroke, in this embodiment, when the piston 21 is located at the top dead center, the side wall of the piston 21 is installed to seal with the second intake hole 12, i.e., the length of the piston 21 is at least greater than 0.5S, so that when the piston 21 moves to the top dead center, the side wall of the piston 21 still blocks the second intake hole 12.

[0036] Furthermore, in this embodiment, the second air intake hole 12 is a round hole. When the cross section of the second air intake hole 12 is circular, the pressure on the inner wall surface is the same, so the force received by the second air intake hole 12 becomes most uniform and the strength becomes the highest.

[0037] Specifically, the method of adjusting the amount of gas supplied to the second air intake hole 12 can be achieved not only by adjusting the opening and closing time of the second air intake hole 12, but also by adjusting the hole diameter of the second air intake hole 12. In this embodiment, the hole diameter of the second air intake hole 12 is D1, where D1≦6 mm.

[0038] Specifically, in this embodiment, the compressor 100 further includes a first intake pipe 3 for connecting the first cooling passage and the first intake hole 11, and a second intake pipe 4 for connecting the second cooling passage and the second intake hole 12. By installing two intake pipes in this manner, two corresponding intake holes and two cooling passages are connected to each other, and the two cooling passages can be installed in parallel to supply refrigerant gas from two routes with different pressures.

[0039] As can be understood, the method of realizing that two refrigerant gases with different pressures enter the cylinder body 1 corresponding to the first intake port 11 and the second intake port 12 is not necessarily limited to using two pipelines as described above, but can also be realized by installing only the first intake pipe 3 to communicate the first cooling passage with the first intake port 11, allowing the high-pressure gas returned from the second cooling passage to directly flow into the housing 5 of the compressor 100, and opening the second intake port 12. When the first intake port 11 is opened, the high-pressure gas in the housing 5 is forced into the cylinder body 1 by the second intake port 12, and similarly, only the second intake pipe 4 is installed to connect the second cooling passage with the second intake port 12 so that the high-pressure gas returned from the first cooling passage can flow directly into the housing 5 of the compressor 100, and when the first intake port 11 is opened, the high-pressure gas in the housing 5 is forced into the cylinder body 1 by the first intake port 11.

[0040] Specifically, since various components such as the cylinder body 1, silencer, and crankcase are installed in the housing 5 of the compressor 100, the internal space is small, and the communication of the second intake pipe 4 is realized and the internal space of the housing 5 can be utilized rationally. In this embodiment, the inner diameter of the second intake pipe 4 is d1, and the outer diameter of the second intake pipe 4 is d2, where 0.3mm≦d1≦6mm and 0.4mm≦d2≦12.5mm. In this way, if the second intake pipe 4 is too thick, it will not interfere with other components, and if it is too thin, it will not affect the amount of gas replenishment. Furthermore, the thickness of the wall of the second intake pipe 4 is accordingly secured to have a certain degree of flexibility while ensuring pneumatic strength not to damage the second intake pipe 4, and to prevent the generation of vibration noise.

[0041] Furthermore, to achieve the above object, the present application further provides a cooling device, and the cooling device includes the compressor 100 described in the above technical solution. For the detailed structure of the compressor 100 of the cooling device, reference can be made to the embodiments of the above compressor 100, and detailed description is omitted here. Since the above compressor 100 is used in the cooling device of the present application, the embodiments of the cooling device of the present application include all the technical solutions of all the embodiments of the above compressor 100, and the achieved technical effects are also all the same, so detailed description is omitted here.

[0042] Note that the specific form of the cooling device is not limited, and it may be a refrigerator, a dehumidifier, or other devices. Specifically, in this embodiment, the cooling device is a refrigerator.

[0043] Furthermore, to enable the normal operation of the compressor 100 and to enable the second intake hole 12 to supply air normally during the intake and compression processes of the cylinder body 1, in this embodiment, the air supply pressure of the first intake hole 11 is set as P1, and the air supply pressure of the second intake hole 12 is set as P2. Here, 1 < P2 / P1 ≤ 6. By installing two parallel flow paths, namely the refrigeration cooling flow path and the refrigeration cooling flow path in this way, the high-temperature and high-pressure refrigerant formed by the compression of the compressor 100 can be reasonably distributed to the cooling flow path and the refrigeration flow path. Thereby, when the cylinder body 1 compresses the refrigerant gas transported to the first intake hole 11, the second intake hole 12 can supply gas to the working chamber 1a, thereby improving the intake air volume of the working chamber 1a of the cylinder body 1, further improving the compression cooling capacity and energy efficiency of the compressor, realizing the respective operating conditions by the two parallel flow paths, and reducing the power consumption.

[0044] The above description is only a preferred embodiment of the present application, and does not limit the patent scope of the present application. Under the inventive concept of the present application, equivalent structural conversions made using the content of the description and the attached drawings of the present application, or direct / indirect applications in other related technical fields are all included in the patent protection scope of the present application.

Explanation of Reference Signs

[0045] 100 Compressor 1 Cylinder body 1a Working chamber 11 First air intake 12 Second air intake 2 Piston components 21 Piston 3 First intake pipe 4 Second intake pipe 5. Housing 6 Exhaust Outer Pipe

Claims

1. A cylinder body, the cylinder cover of the cylinder body being provided with a first intake hole for communicating with a first cooling passage; a piston component including a piston movably mounted within the cylinder body, a working chamber being formed between the piston and a bottom of the cylinder body, the piston having a top dead center close to a cylinder cover of the cylinder body and a bottom dead center far from a cylinder cover of the cylinder body in a moving stroke, the distance between the top dead center and the bottom dead center being S; A compressor, wherein the cylinder body or the piston is provided with a second intake hole to be installed so as to communicate with a second cooling passage, the second intake hole is installed so as to communicate with the working chamber when the piston moves to a set position, and at the set position, a distance between the piston and the top dead center is L1, and L1>0.5S.

2. A second intake hole is formed through the side wall of the cylinder body, 2. The compressor according to claim 1, wherein a distance between the second intake port and the top dead center is L2, and L2>0.5S.

3. The compressor of claim 2 , wherein a side wall of the piston covers and seals the second intake port when the piston is at the top dead center.

4. The compressor of claim 2 , wherein the second intake hole is a round hole.

5. The compressor according to claim 2 , wherein the hole diameter of the second intake hole is D1, and D1≦6 mm.

6. 2. The compressor according to claim 1, further comprising: a first intake pipe for communicating the first cooling passage with the first intake hole; and a second intake pipe for communicating the second cooling passage with the second intake hole.

7. 7. The compressor according to claim 6, wherein an inner diameter of the second intake pipe is d1, an outer diameter of the second intake pipe is d2, 0.3 mm≦d1≦6 mm, and 0.4 mm≦d2≦12.5 mm.

8. A refrigeration device comprising the compressor according to any one of claims 1 to 7.

9. The cooling appliance according to claim 8 , wherein the cooling appliance is a refrigerator.

10. 10. The cooling device according to claim 9, wherein the supply pressure of the first intake hole is P1, the supply pressure of the second intake hole is P2, and 1<P2 / P1≦6.

Images