WO2023155313A1 - 压缩气缸、压缩机及制冷设备 - Google Patents
压缩气缸、压缩机及制冷设备 Download PDFInfo
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- WO2023155313A1 WO2023155313A1 PCT/CN2022/093373 CN2022093373W WO2023155313A1 WO 2023155313 A1 WO2023155313 A1 WO 2023155313A1 CN 2022093373 W CN2022093373 W CN 2022093373W WO 2023155313 A1 WO2023155313 A1 WO 2023155313A1
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- suction hole
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
Definitions
- the present application relates to the technical field of refrigeration, in particular to a compression cylinder, a compressor and refrigeration equipment.
- the existing reciprocating compressor has experienced decades of development, and its performance level has also tended to be a bottleneck.
- the single-suction and single-discharge compression pump body mechanism is very mature, but it still lacks innovative and breakthrough technological progress in the face of future requirements for greatly improving the performance of the compressor.
- the double-suction compressor can effectively improve the energy efficiency of the refrigeration system and reduce power consumption, but when supplementing the working chamber of the compressor cylinder through the second suction hole, the general direct suction hole adopts a larger When the diameter of the hole is straight, the air supply flow rate is too large, and the air supply volume is likely to exceed the air supply volume required to pass through the cylinder. When it is too narrow, the flow resistance of high-pressure gas becomes larger, the pressure flow loss also increases, and the pressurization effect is not good.
- the application proposes a compressed air cylinder, wherein the compressed air cylinder includes:
- the cylinder block includes a working chamber formed inside it, the bottom of the working chamber is provided with a first suction hole, and the side wall is provided with a second suction hole; and,
- the second suction hole is disposed adjacent to the bottom dead center
- the minimum diameter of the section of the tapered hole section is D1, wherein, D1 ⁇ 3mm.
- the minimum diameter of the section of the tapered hole section is D2, wherein, D2 ⁇ 2mm.
- the cross-section of the second suction hole is circular or elliptical.
- the present application also provides a compressor, the compressor includes the above-mentioned compression cylinder, and the compression cylinder includes:
- a cylinder block, the cylinder head of the cylinder block is provided with a first air suction hole, and the side wall of the cylinder block is also provided with a second air suction hole;
- the piston assembly includes a piston movably arranged in the cylinder body, a working chamber is formed between the piston and the bottom of the cylinder body, and the piston has an upper side of the cylinder head close to the cylinder body during the movable stroke. dead center and the bottom dead center of the cylinder head away from the cylinder block, the second air suction hole is located between the top dead center and the bottom dead center;
- the second air suction hole includes a tapered hole section, and the tapered hole section is tapered from the outside to the inside of the cylinder body.
- the present application also provides a refrigeration device, which includes the above-mentioned compressor, and the compressor includes the above-mentioned compression cylinder, wherein the compression cylinder includes:
- the cylinder body includes a working chamber formed inside it, the bottom of the working chamber is provided with a first suction hole, and the side wall is provided with a second suction hole; and,
- the piston assembly includes a piston movable in the working chamber, and the piston has a top dead center at the bottom of the inner cavity of the cylinder body and a bottom dead center far away from the bottom of the inner cavity of the cylinder body during the movable stroke ;
- the refrigeration device is a refrigerator.
- the compression cylinder includes a cylinder body and a piston assembly
- the cylinder body includes a working chamber formed inside it, the bottom of the working chamber is provided with a first suction hole, and the side wall is provided with a second suction hole.
- Two suction holes the piston assembly includes a piston movably arranged in the working chamber, and the piston has a top dead center at the bottom of the inner cavity of the cylinder body and an inner hole far away from the cylinder body during the movable stroke.
- the second suction hole adopts a straight hole with a larger aperture, the flow rate of the air supply is too large, and the amount of air supply will easily exceed the amount of air supply required to pass through the cylinder. If in order to make the amount of supplementary air within the set range, when the second suction hole adopts a straight hole with a smaller aperture, the flow rate of the supplementary air reaches the standard, but when the aperture is too narrow, the flow resistance of the high-pressure gas becomes larger, The pressure flow loss also increases, and the pressurization effect is not good. If the second suction hole is set as a stepped hole, when the high-pressure gas flows from the large-aperture section into the small-aperture section, the cross-sectional mutation is large, and the flow resistance suddenly increases.
- Fig. 2 is a partial cross-sectional schematic diagram of the compression cylinder (the second air suction hole is opened) in Fig. 1;
- Fig. 3 is a schematic structural view of the second air suction hole in Fig. 1;
- Fig. 4 is a schematic cross-sectional view of the second air suction hole in Fig. 1 when it is close to the bottom dead center (the second air suction hole is closed);
- Fig. 7 is a partial cross-sectional schematic diagram of an embodiment of the compressor provided by the present application.
- the existing reciprocating compressor has experienced decades of development, and its performance level has also tended to be a bottleneck.
- the single-suction and single-discharge compression pump body mechanism is very mature, but it still lacks innovative and breakthrough technological progress in the face of future requirements for greatly improving the performance of the compressor.
- the double-suction compressor can effectively improve the energy efficiency of the refrigeration system and reduce power consumption, but when supplementing the working chamber of the compressor cylinder through the second suction hole, the general direct suction hole adopts a larger When the diameter of the hole is straight, the air supply flow rate is too large, and the air supply volume is likely to exceed the air supply volume required to pass through the cylinder. When it is too narrow, the flow resistance of high-pressure gas becomes larger, the pressure flow loss also increases, and the pressurization effect is not good.
- the present application provides a compression cylinder 100, and Fig. 1 to Fig. 6 are specific embodiments of the compression cylinder 100 provided in the present application.
- the piston assembly 2 includes a piston 21 movable in the working chamber 1a, and the piston 21 has a top dead center located at the bottom of the inner cavity of the cylinder 1 and an inner wall far away from the cylinder 1 during the movable stroke. Bottom dead center at the bottom of the cavity, the second suction hole 12 is located between the top dead center and the bottom dead center;
- the compression cylinder 100 includes a cylinder body 1 and a piston assembly 2, the cylinder body 1 includes a working chamber 1a formed inside it, and the bottom of the working chamber 1a is provided with a first suction hole 11 , and the side wall is provided with a second suction hole 12, the piston assembly 2 includes a piston 21 that is movable in the working chamber 1a, and the piston 21 has an inner cavity located in the cylinder body 1 during the active stroke.
- the air hole 12 is opened, and the refrigerant to be compressed can be transported to the working chamber 1a through the first air suction hole 11 and the second air suction hole 12 at the same time.
- the second suction hole 12 adopts a straight hole with a larger aperture diameter, the flow rate of the supplementary air is too large, and the amount of supplementary air is easily exceeded. 1.
- the required air supply volume If the second suction hole 12 adopts a straight hole with a smaller aperture in order to make the air supply volume within the set range, the flow rate of the air supply can reach the standard, but when the aperture is too narrow, The flow resistance of the high-pressure gas increases, the pressure flow loss also increases, and the pressurization effect is not good. If the second suction hole 12 is set as a stepped hole, when the high-pressure gas flows into the small-aperture section from the large-aperture section, the sudden change in cross-section is relatively small.
- the aperture setting of the side of the second suction hole 12 close to the inner wall of the cylinder body 1 can be set It is set within the set range so that the input flow rate of supplementary air reaches the standard, and the inner diameter of the tapered hole section 12a is gradually reduced, so that the flow resistance does not change significantly, so as to provide a kind of , a compression cylinder 100 capable of reducing flow resistance.
- the second suction hole 12 communicates with the second suction inner tube, and the second suction inner tube communicates with the external condensation circuit to provide high-pressure refrigerant gas, the second suction hole 12
- the end with a larger inner diameter is in order to adapt to the communication of the second suction inner pipe, and the smaller end with the inner diameter of the second suction hole 12 is used to adjust the flow rate.
- the tapered change rate of the tapered hole section 12a If it is too large, the flow resistance of the same gas is relatively large, and the tapered rate of change is too small, and the second suction hole 12 has not yet reached the reduced aperture size, and has been sprayed into the working chamber 1a, and the flow rate of the gas too large, in order to make the rate of change of the tapered hole section 12a reach the best working condition, in this embodiment, the tapered hole section 12a is at the angle formed between two opposite inner walls is ⁇ , where 50° ⁇ 150°.
- the compression cylinder 100 realizes the cooling function of freezing and refrigerating through one flow path, so that when the freezing room or the cold room needs to be refrigerated, the entire heat exchange system needs to participate in the work, which makes the energy consumption larger and the energy efficiency is relatively high. Low.
- the compression cylinder 100 provided by this application, 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 compression cylinder 100 can be reasonably distributed to the freezing flow path and the refrigerating flow path, after the high-temperature and high-pressure refrigerant formed by the compression of the compression cylinder 100 passes through the evaporator corresponding to the freezing chamber, the temperature and pressure are relatively low when it returns to the compression cylinder 100, and the compression cylinder 100 After the high-temperature and high-pressure refrigerant compressed by 100 passes through the evaporator corresponding to the refrigerating room, the temperature and pressure are relatively high when it returns to the compression cylinder 100, and the working chamber 1a of the cylinder 1 is simultaneously connected to the first A suction hole 11 and the second suction hole 12, so as to be able to pass through the first suction flow passage corresponding to the first suction hole 11, and the second suction flow corresponding to the second suction hole 12 In this way, the relatively low
- the high-pressure refrigerant is delivered to the compression cylinder 100 through the second suction hole 12, so that when the cylinder 1 compresses the refrigerant gas delivered by the first suction hole 11, the second suction hole 12 Air can be added to the working chamber 1a, thereby increasing the suction capacity of the working chamber 1a of the cylinder body 1, thereby improving the compression energy efficiency of the compression cylinder 100, and realizing it through two parallel flow paths Respective working conditions, reduce power consumption.
- the distance between the second air suction hole 12 and the top dead center is L
- the distance between the top dead center and the bottom dead center is S, wherein, 0.5 S ⁇ L.
- the suction stroke of the cylinder including:
- First stroke the piston 21 moves from the top dead center to the bottom dead center, and the distance from the top dead center is less than 0.5S.
- the control valve group is opened, so that the first suction hole 11 is connected, and the second suction hole 12 is blocked by the piston 21 .
- the working chamber 1 a of the cylinder body 1 only realizes air suction through the first air suction hole 11 .
- the total amount of refrigerant in the working chamber 1 a comes from the first suction hole 11 , that is, the refrigerant in the first condensation circuit.
- Second stroke when the piston 21 moves from the top dead center to the second bottom dead center, and the distance from the top dead center is greater than 0.5S.
- the piston 21 does not block the second suction hole 12 , so that the second suction hole 12 communicates with the working chamber 1 a of the cylinder 1 .
- the control valve group is switched between an open state and a closed state according to actual requirements.
- the control valve group is in an open state, the first air suction hole 11 and the second air suction hole 12 input airflow to the working chamber 1 a of the cylinder body 1 at the same time.
- the distance from the second suction hole 12 to the top dead center is greater than 0.5S, that is, the distance to the first suction hole 11 is greater than 0.5S, so that there is a suitable buffer distance between the two.
- the obstruction effect of the airflow of the second suction hole 12 on the airflow of the first suction hole 11 is alleviated, and the compression energy efficiency is improved.
- the high-pressure refrigerant provided by the second condensing circuit lasts for a long time, and the amount of supplementary air is large; when the second suction hole 12 is closer to the bottom dead center, the opening time of the second suction hole 12 is later, and the closing time is earlier,
- the high-pressure refrigerant provided by the second condensing circuit has a short time and a short air replenishment time, so the air replenishment amount is also small.
- the position of the second air suction hole 12 can be set according to the requirement of the amount of supplementary air.
- the compression stroke of the cylinder including:
- the piston 21 moves from the bottom dead center to the direction close to the top dead center, and the distance from the top dead center is greater than 0.5S.
- the control valve group is closed, and the piston 21 moves rapidly toward the top dead center.
- the second air suction hole 12 still supplies airflow to the working chamber 1 a of the cylinder body 1 .
- the refrigerant replenished into the working chamber 1 a comes from the second suction hole 12 . Therefore, in the third stroke, when the airflow in the working chamber 1a of the cylinder body 1 is compressed, the air flow input into the working chamber 1a of the cylinder body 1 through the second suction hole 12 will not be hindered excessively.
- Airflow so that the cylinder 1 can still inhale airflow during the compression stroke. And, because the airflow from the first suction hole 11 and the second suction hole 12 is mixed in the working chamber 1a of the cylinder body 1, the pressure of the airflow in the working chamber 1a of the cylinder body 1 is less than Through the airflow pressure in the second suction hole 12 .
- the piston 21 moves from the bottom dead center to the direction close to the top dead center, and the distance from the top dead center is less than 0.5S.
- the control valve group is still closed, and the piston 21 blocks the second suction hole 12 .
- the piston 21 compresses the airflow in the working chamber 1a of the cylinder 1 into a high-pressure airflow.
- the airflow pressure in the working chamber 1a of the cylinder 1 is compressed to a certain position.
- the control valve group connected to the output pipeline of the working chamber 1a of the cylinder 1 is switched from the closed state to the open state to output the compressed high-pressure air flow.
- the working lines of the compression cylinder 100 corresponding to the two condensing flow paths are:
- the flow path of the air flow in the first suction flow path is: the first condensation flow path ⁇ the first suction hole 11 ⁇ the working chamber 1a of the cylinder body 1 .
- the air flow path in the second suction flow path is: the second condensation flow path ⁇ the second suction hole 12 ⁇ the working chamber 1a of the cylinder body 1 .
- the compression cylinder 100 also includes an inner exhaust pipe communicating with the working chamber 1a of the cylinder body 1, and the inner exhaust pipe is used to communicate with the exhaust outer pipe to compress the working chamber 1a of the cylinder body 1 Good high-pressure air flow is discharged from the inner exhaust pipe to the outer exhaust pipe.
- the first suction hole 11 is mainly opened for main suction, which can suck a large amount of refrigerant on the condensation flow path corresponding to the freezing chamber.
- all The second suction hole 12 communicates with the working chamber 1a, the first suction hole 11 is closed, and the second suction hole 12 starts to replenish high-pressure refrigerant gas, and continues to replenish gas in the first half of the stroke of the compression stage , and finally in the second half of the compression stroke, the second suction hole 12 is closed, and the piston 21 compresses the refrigerant in the working chamber 1a.
- the piston 21 can be During the reciprocating movement, the opening and closing time of the second air suction hole 12 is adjusted, so as to realize the adjustment of the flow ratio of the first air suction hole 11 and the second air suction hole 12 . And by setting the second suction hole 12 on the side wall of the cylinder body 1 and close to the bottom dead center, the compression cylinder 100 does not need to be specially provided with a control valve group to control the second suction hole.
- the opening and closing of the air hole 12 can realize the automatic opening and closing of the second air suction hole 12 during the movable stroke of the piston 21, the structure design is ingenious, and the cost is also saved.
- the distance between the top dead center and the bottom dead center is S, that is, the top dead center refers to the position where the piston 21 is close to the cylinder 1.
- the top dead center refers to the position where the piston 21 is close to the cylinder 1.
- the bottom dead center refers to the position of the end of the cylinder block 1.
- the distance S is the distance between the two limit states of the end surface of the piston 21 close to the bottom wall of the cylinder 1 .
- the distance between the second suction hole 12 and the top dead center is L, that is, the distance between the centerline of the second suction hole 12 and the top dead center is L.
- the second suction hole 12 is located between the top dead center and the bottom dead center, and is adjacent to the bottom dead center.
- the second air suction hole 12 is adjacent to the bottom dead center, relative to setting the second air suction hole 12 close to the midpoint between the top dead center and the bottom dead center, when When the piston 21 moves from the top dead center to the bottom dead center, the first suction hole 11 is opened, and the first suction hole 11 communicates with the first suction of external high-pressure refrigerant gas.
- the tube inputs high-pressure gas with a certain pressure P1.
- the volume V1 inside the working chamber 1a is larger than that when the second suction hole 12 is set close to the The volume V2 inside the working chamber 1a near the midpoint between the top dead center and the bottom dead center, so that when the first air suction hole 11 is inhaled to work, the pressure Pa in the cylinder body 1 is relatively small, The pressure P2 at the inlet of the second suction hole 12 is greater than Pa, and the pressure difference ⁇ Pa is relatively large.
- the gas-liquid flow rate The limit is the speed of sound under the condition of pressure and temperature at that time, and the transmission speed of sound waves represents the limit of the medium's stable transmission force under the condition of pressure and temperature at that time.
- the density will be greatly reduced. increase, it will cause congestion in the pipeline, so that the speed of the fluid cannot reach the speed of sound. No matter how pressurized, the flow rate of the gas and liquid will no longer increase.
- the flow velocity of the gas reaches the critical flow velocity c fc , that is, reaches the local speed of sound.
- the flow velocity and air pressure of the gas are in a constant state, so the air pressure in the second air suction hole 12 is at a stable critical pressure value P0, the flow velocity of the second suction hole 12 into the working chamber 1a at this moment is the local speed of sound, the pressure and flow velocity generated by the second suction hole 12 are controlled within a constant range, and the reduction
- the flow rate of the hole section 12a is related to the minimum diameter D of the section of the tapered hole section 12a.
- the minimum diameter of the section of the tapered hole section 12a is D1, wherein, D1 ⁇ 3mm, the second When the air suction hole 12 is arranged adjacent to the bottom dead center, the second air suction hole 12 must be in the open state for a short time during the reciprocating movement of the piston 21, so that the second air suction hole 12
- the minimum cross-sectional diameter of the cross-section is set appropriately larger to adjust the total amount of air supply.
- D1 ⁇ 3mm the minimum diameter of the cross-section of the tapered hole segment 12a can be adjusted according to the air supply volume required to ensure that the air supply The total volume of air exceeds the total amount of supplementary air required.
- the solution of this embodiment is applicable to the compressor 200 with a small amount of supplementary air.
- the critical pressure P0 refers to the pressure (pressure) when a substance is in a critical state. It is the minimum pressure required to liquefy a gas at the critical temperature. That is, the saturated vapor pressure of a liquid at its critical temperature. At critical temperature and critical pressure, the molar volume of a substance is called critical molar volume. The state at critical temperature and critical pressure is called critical state. Corresponding to this application, that is, the saturated vapor pressure of the refrigerant.
- the second suction hole 12 is located between the top dead center and the bottom dead center, and is adjacent to the middle of the top dead center and the bottom dead center.
- the first suction hole 11 is opened, and the first suction pipe connected to the first suction hole 11 communicates with the external high-pressure refrigerant gas to input high-pressure gas with a certain pressure P1.
- the volume V2 inside the working chamber 1a is smaller than the volume V1 inside the working chamber 1a when the second suction hole 12 is set close to the bottom dead center , so that when the first air suction hole 11 is inhaled, the pressure Pb in the cylinder 1 is relatively large, that is, Pb>Pa, and the pressure P2 at the inlet of the second air suction hole 12 is greater than Pb, and the pressure difference ⁇ Pb Smaller, that is, ⁇ Pb ⁇ Pa, at this moment, the Pb in the working chamber 1a is greater than the critical pressure value P0, and when Pb>P0, it also shows that the second suction hole 12 enters the working chamber 1a at this moment.
- the flow velocity is always below the local speed of sound.
- the second air suction hole 12 is set adjacent to the midpoint between the top dead center and the bottom dead center, the second air suction hole 12 must be opened during the reciprocating movement of the piston 21.
- the time in the state is longer, so the minimum cross-sectional diameter D2 of the second suction hole 12 is set appropriately smaller to adjust the total amount of air supply, in order to adjust the tapered hole section according to the amount of air supply required.
- the minimum cross-sectional diameter of 12a ensures that the total amount of supplementary air exceeds the required total volume of supplementary air
- the minimum cross-sectional diameter of the tapered hole segment 12a is D2, wherein D2 ⁇ 2mm.
- the solution of this embodiment is applicable to the compressor 200 that requires a large amount of supplementary air.
- the second suction hole 12 is set on the wall surface of the crankcase cylinder block 1 hole of the compressor 200, the thickness of the wall surface of the crankcase cylinder block 1 hole of the compressor 200 and the length of the tapered hole section 12a It is not necessarily in a state of complete matching.
- the second suction hole 12 also includes two straight hole sections 12b communicated with the two ends of the tapered hole section 12a, which can be passed through
- the two straight hole sections 12b are transitionally adjusted, that is, when the length of the tapered hole section 12a needs to be set longer, the length of the two straight hole sections 12b can be set shorter, otherwise, when When the length of the tapered hole section 12a needs to be set relatively short, the length of the two straight hole sections 12b can be set longer.
- the cross section of the second suction hole 12 is circular or elliptical.
- the pressure on the inner wall surface is the same, so that the stress of the second air suction hole 12 is the most uniform and the strength is the highest.
- the present application also proposes a compressor 200, which includes the compression cylinder 100 described in the above technical solution.
- the detailed structure of the compression cylinder 100 of the compressor 200 can refer to the embodiment of the above-mentioned compression cylinder 100, which will not be repeated here; since the above-mentioned compression cylinder 100 is used in the compressor 200 of the present application, therefore
- the embodiments of the compressor 200 of the present application include all the technical solutions of all the embodiments of the above-mentioned compression cylinder 100, and the achieved technical effects are also completely the same, which will not be repeated here.
- the present application also proposes a refrigeration device, which includes the compressor 200 described in the above technical solution.
- the detailed structure of the compressor 200 of the refrigeration equipment can refer to the embodiment of the above-mentioned compressor 200, which will not be repeated here; since the above-mentioned compressor 200 is used in the refrigeration equipment of the present application, therefore, this
- the embodiments of the application for refrigeration equipment include all the technical solutions of all the embodiments of the above-mentioned compressor 200, and the achieved technical effects are also completely the same, which will not be repeated here.
- the specific form of the refrigeration equipment is not limited, and it may be an air conditioner, a fresh air fan, or other equipment.
- the refrigeration device is a refrigerator.
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Abstract
一种压缩气缸、压缩机及制冷设备，压缩气缸(100)包括缸体(1)和活塞组件(2)，缸体(1)的工作腔(1a)的底部设置有第一吸气孔(11)，且侧壁设置有第二吸气孔(12)。活塞组件(2)包括活动设于工作腔(1a)内的活塞(21)，活塞(21)在活动行程中具有位于缸体(1)的内腔底部的上止点及远离缸体(1)的内腔底部的下止点。第二吸气孔(12)包括渐缩孔段(12a)，渐缩孔段(12a)自缸体(1)的外侧向内侧的方向呈渐缩设置。该压缩气缸通过将渐缩孔段(12a)设置为渐缩的形式，使得第二吸气孔(12)靠近缸体内壁的一侧的孔径的设定可以设置在设定范围内，使得补气的输入流量达到标准，且渐缩孔段(12a)的内径逐步减小，不会使流动阻力有明显的突变，以在保证补气量的同时，能够减少流动阻力。
Description
优先权信息
本申请要求于2022年2月18日申请的、申请号为202210155390.4以及202220342616.7的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
本申请涉及制冷技术领域，尤其是涉及一种压缩气缸、压缩机及制冷设备。
随着全球碳排放的限制升级，制冷行业对节能减排要求不断提高。压缩机作为制冷系统的最核心部件和耗能大件，需要对其的制冷性能和能效水平提出更高要求。
现有往复式压缩机经历几十年的发展，其性能水平的提升也趋于瓶颈。单吸气单排气压缩泵体机构已十分成熟，但面临未来对压缩机的性能大幅提升的要求，仍缺乏创新性和突破性的技术进步。而双吸气压缩机可以有效提高制冷系统能效、降低功率消耗，但是在通过第二吸气孔对压缩机缸体的工作腔内进行补气的时候，一般的直吸气孔采用较大的孔径的直孔时，补气的流量过大，补气量容易超过通过缸体所需的补气量，第二吸气孔采用较小的孔径的直孔时，补气的流量达到标准，但是孔径过于狭小时，高压气体的流动阻力变大，压力流动损失也增加，增压效果不好。
发明内容
本申请的主要目的是提出一种压缩气缸、压缩机及制冷设备，旨在提供一种在保证补气量的同时，能够减少流动阻力的压缩气缸。
为实现上述目的，本申请提出的一种压缩气缸，其中所述压缩气缸包括：
缸体，包括形成于其内部的工作腔，所述工作腔的底部设置有第一吸气 孔，且侧壁设置有第二吸气孔；以及，
活塞组件，包括活动设于所述工作腔内的活塞，所述活塞在活动行程中具有位于所述缸体的内腔底部的上止点及远离所述缸体的内腔底部的下止点，所述第二吸气孔位于所述上止点和所述下止点之间；
其中，所述第二吸气孔包括渐缩孔段，所述渐缩孔段自所述缸体的外侧向内侧的方向呈渐缩设置。
在一实施例中，所述渐缩孔段呈相对设置的两个内壁之间形成的夹角度数为α，其中，50°≤α≤150°。
在一实施例中，所述第二吸气孔与所述上止点的距离为L，所述上止点与所述下止点之间的距离为S，其中，0.5S＜L。
在一实施例中，所述第二吸气孔邻近所述下止点设置；
所述渐缩孔段的截面最小孔径为D1，其中，D1≤3mm。
在一实施例中，所述第二吸气孔邻近所述上止点与所述下止点的中点设置；
所述渐缩孔段的截面最小孔径为D2，其中，D2≤2mm。
在一实施例中，所述第二吸气孔还包括与所述渐缩孔段的两端分别连通设置的两个直孔段。
在一实施例中，所述第二吸气孔的截面呈圆形或椭圆形。
本申请还提供一种压缩机，所述压缩机包括上述的压缩气缸，所述压缩气缸包括：
缸体，所述缸体的汽缸盖设置有第一吸气孔，所述缸体的侧壁上还设置有第二吸气孔；以及，
活塞组件，包括活动设于所述缸体内的活塞，所述活塞与所述缸体的底部之间形成工作腔，所述活塞在活动行程中具有位于靠近所述缸体的汽缸盖的上止点及远离所述缸体的汽缸盖的下止点，所述第二吸气孔位于所述上止点和所述下止点之间；
其中，所述第二吸气孔包括渐缩孔段，所述渐缩孔段自所述缸体的外侧向内侧的方向呈渐缩设置。
本申请还提供一种制冷设备，所述制冷设备包括上述的压缩机，所述压缩机包括上述的压缩气缸，其中，所述压缩气缸包括：
缸体，包括形成于其内部的工作腔，所述工作腔的底部设置有第一吸气孔，且侧壁设置有第二吸气孔；以及，
活塞组件，包括活动设于所述工作腔内的活塞，所述活塞在活动行程中具有位于所述缸体的内腔底部的上止点及远离所述缸体的内腔底部的下止点；
其中，所述第二吸气孔包括渐缩孔段，所述渐缩孔段自所述缸体的外侧向内侧的方向呈渐缩设置。
在一实施例中，所述制冷设备为冰箱。
本申请提供的技术方案中，压缩气缸包括缸体和活塞组件，所述缸体包括形成于其内部的工作腔，所述工作腔的底部设置有第一吸气孔，且侧壁设置有第二吸气孔，所述活塞组件包括活动设于所述工作腔内的活塞，所述活塞在活动行程中具有位于所述缸体的内腔底部的上止点及远离所述缸体的内腔底部的下止点，所述第二吸气孔位于所述上止点和所述下止点之间，当所述活塞处于上止点的时候，所述第二吸气孔被活塞的侧部堵塞，待压缩的冷媒可以经所述第一吸气孔输送至所述工作腔，在所述活塞处于下止点的时候，活塞远离所述第二吸气孔，所述第二吸气孔被打开，待压缩的冷媒可以经所述第一吸气孔和所述第二吸气孔同时输送至所述工作腔，因所述第二吸气孔的补气量与孔径的大小有着直接的关系，孔径越大，流量越大，若所述第二吸气孔采用较大的孔径的直孔时，补气的流量过大，补气量容易超过通过缸体所需的补气量，若为了使得补气量能够在设定范围内，所述第二吸气孔采用较小的孔径的直孔时，补气的流量达到标准，但是孔径过于狭小时，高压气体的流动阻力变大，压力流动损失也增加，增压效果不好，若将第二吸气孔设置为台阶孔，在高压气体从大孔径段流入小孔径段的时候，截面突变较大，同样流动阻力突然变大，通过将所述渐缩孔段设置为渐缩的形式，使得所述第二吸气孔靠近所述缸体内壁的一侧的孔径的设定可以设置在设定范围内，使得补气的输入流量达到标准，并且所述渐缩孔段的内径逐步减小，不会使得流动阻力有明显的突变，以提供一种在保证补气量的同时，能够减少流动阻力的压缩气缸。
为了更清楚地说明本申请实施例或现有技术中的技术方案，下面将对实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图示出的结构获得其他的附图。
图1为本申请提供的压缩气缸一实施例(第二吸气孔关闭状态)的部分截面意图；
图2为图1中的压缩气缸(第二吸气孔打开状态)的部分截面示意图；
图3为图1中的第二吸气孔的结构示意图；
图4为图1中的第二吸气孔邻近下止点时(第二吸气孔关闭状态)的剖面示意图；
图5为图1中的第二吸气孔邻近下止点时(第二吸气孔打开状态)的剖面示意图；
图6为图1中的第二吸气孔邻近上止点和下止点中点时(第二吸气孔打开状态)的剖面示意图；
图7为本申请提供的压缩机的一实施例的部分截面示意图。
附图标号说明：
| 标号 | 名称 | 标号 | 名称 |
| 100 | 压缩气缸 | 12a | 渐缩孔段 |
| 1 | 缸体 | 12b | 直孔段 |
| 1a | 工作腔 | 2 | 活塞组件 |
| 11 | 第一吸气孔 | 21 | 活塞 |
| 12 | 第二吸气孔 | 200 | 压缩机 |
本申请目的的实现、功能特点及优点将结合实施例，参照附图做进一步说明。
下面将结合本申请实施例中的附图，对本申请实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例仅仅是本申请的一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有作出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
需要说明，若本申请实施例中有涉及方向性指示(诸如上、下、左、右、前、后……)，则该方向性指示仅用于解释在某一特定姿态(如附图所示)下各部件之间的相对位置关系、运动情况等，如果该特定姿态发生改变时，则该方向性指示也相应地随之改变。
另外，若本申请实施例中有涉及“第一”、“第二”等的描述，则该“第一”、“第二”等的描述仅用于描述目的，而不能理解为指示或暗示其相对重要性或者隐含指明所指示的技术特征的数量。由此，限定有“第一”、“第二”的特征可以明示或者隐含地包括至少一个该特征。另外，全文中出现的“和/或”的含义，包括三个并列的方案，以“A和/或B”为例，包括A方案、或B方案、或A和B同时满足的方案。另外，各个实施例之间的技术方案可以相互结合，但是必须是以本领域普通技术人员能够实现为基础，当技术方案的结合出现相互矛盾或无法实现时应当认为这种技术方案的结合不存在，也不在本申请要求的保护范围之内。
现有往复式压缩机经历几十年的发展，其性能水平的提升也趋于瓶颈。单吸气单排气压缩泵体机构已十分成熟，但面临未来对压缩机的性能大幅提升的要求，仍缺乏创新性和突破性的技术进步。而双吸气压缩机可以有效提高制冷系统能效、降低功率消耗，但是在通过第二吸气孔对压缩机缸体的工作腔内进行补气的时候，一般的直吸气孔采用较大的孔径的直孔时，补气的流量过大，补气量容易超过通过缸体所需的补气量，第二吸气孔采用较小的孔径的直孔时，补气的流量达到标准，但是孔径过于狭小时，高压气体的流动阻力变大，压力流动损失也增加，增压效果不好。
为了解决上述问题，本申请提供一种压缩气缸100，图1至图6为本申请提供的压缩气缸100的具体实施例。
请参阅图1至图3，所述压缩气缸100包括缸体1和活塞组件2，所述缸体1包括形成于其内部的工作腔1a，所述工作腔1a的底部设置有第一吸气孔 11，且侧壁设置有第二吸气孔12；以及，
活塞组件2，包括活动设于所述工作腔1a内的活塞21，所述活塞21在活动行程中具有位于所述缸体1的内腔底部的上止点及远离所述缸体1的内腔底部的下止点，所述第二吸气孔12位于所述上止点和所述下止点之间；
其中，所述第二吸气孔12包括渐缩孔段12a，所述渐缩孔段12a自所述缸体1的外侧向内侧的方向呈渐缩设置。
本申请提供的技术方案中，压缩气缸100包括缸体1和活塞组件2，所述缸体1包括形成于其内部的工作腔1a，所述工作腔1a的底部设置有第一吸气孔11，且侧壁设置有第二吸气孔12，所述活塞组件2包括活动设于所述工作腔1a内的活塞21，所述活塞21在活动行程中具有位于所述缸体1的内腔底部的上止点及远离所述缸体1的内腔底部的下止点，当所述活塞21处于上止点的时候，所述第二吸气孔12被活塞21的侧部堵塞，待压缩的冷媒可以经所述第一吸气孔11输送至所述工作腔1a，在所述活塞21处于下止点的时候，活塞21远离所述第二吸气孔12，所述第二吸气孔12被打开，待压缩的冷媒可以经所述第一吸气孔11和所述第二吸气孔12同时输送至所述工作腔1a，因所述第二吸气孔12的补气量与孔径的大小有着直接的关系，孔径越大，流量越大，若所述第二吸气孔12采用较大的孔径的直孔时，补气的流量过大，补气量容易超过通过缸体1所需的补气量，若为了使得补气量能够在设定范围内，所述第二吸气孔12采用较小的孔径的直孔时，补气的流量达到标准，但是孔径过于狭小时，高压气体的流动阻力变大，压力流动损失也增加，增压效果不好，若将第二吸气孔12设置为台阶孔，在高压气体从大孔径段流入小孔径段的时候，截面突变较大，同样流动阻力突然变大，通过将所述渐缩孔段12a设置为渐缩的形式，使得所述第二吸气孔12靠近所述缸体1内壁的一侧的孔径的设定可以设置在设定范围内，使得补气的输入流量达到标准，并且所述渐缩孔段12a的内径逐步减小，不会使得流动阻力有明显的突变，以提供一种在保证补气量的同时，能够减少流动阻力的压缩气缸100。
具体地，因所述第二吸气孔12与所述第二吸气内管连通，第二吸气内管与外部的冷凝回路连通，以提供高压冷媒气体，所述第二吸气孔12内径较大的一端为了适配所述第二吸气内管的连通，所述第二吸气孔12内径较小的一端为了调节流量的大小，所述渐缩孔段12a的渐缩变化率若过于大，同样的 气体的流动阻力较大，渐缩变化率过小，所述第二吸气孔12还未达到缩减的孔径大小，就已经被喷入至工作腔1a中，气体的流量过大，为了使得所述渐缩孔段12a的变化率能够达到最佳的工作状态，在本实施例中，所述渐缩孔段12a呈相对设置的两个内壁之间形成的夹角度数为α，其中，50°≤α≤150°。
以所述压缩气缸100用于冰箱的制冷系统为例进行说明，因冰箱在制冷过程中，高温高压冷媒气体自压缩气缸100输送至对应的冷冻室和冷藏室的蒸发器进行蒸发吸热，实现冷冻室和冷藏室的制冷，但是冷冻室和冷藏室设置的温度不一致，两者蒸发温度不一样，冷媒在冷冻室和冷藏室进行换热后的温度和压力不相同，并且现有技术中，压缩气缸100通过一个流路实现冷冻和冷藏的制冷功能，这样不管是冷冻室或是冷藏室需要进行制冷的时候，整个换热系统都需要参与到工作中，使得能耗消耗较大，能效比较低。
本申请提供的压缩气缸100中，通过设置两个并联的流路，即冷冻冷凝流路和冷藏冷凝流路，即所述压缩气缸100将压缩形成的高温高压冷媒可以合理的分配至冷冻流路和冷藏流路，因所述压缩气缸100压缩形成的高温高压冷媒经冷冻室对应的蒸发器后，其回至所述压缩气缸100时的温度较低，且压力较小，而所述压缩气缸100压缩形成的高温高压冷媒经冷藏室对应的蒸发器后，其回至所述压缩气缸100时的温度较高，且压力较大，将所述缸体1的工作腔1a同时连通所述第一吸气孔11及所述第二吸气孔12，以能够通过所述第一吸气孔11对应的第一吸气流道，所述第二吸气孔12对应的第二吸气流道，这样将冷冻室回流的相对较低温较低压力的冷媒通过所述第一吸气孔11输送至所述压缩气缸100的所述缸体1内，而将冷藏室回流的相对较高温较高压力的冷媒通过所述第二吸气孔12输送至所述压缩气缸100，这样在所述缸体1对第一吸气孔11输送的冷媒气体压缩时，所述第二吸气孔12可以对所述工作腔1a内进行补气，从而提高了所述缸体1的工作腔1a的吸气量，进而提高所述压缩气缸100的压缩能效，并且通过两个并联的流路来实现各自的工况条件，降低功率消耗。
因在常规的压缩机中往往需要通过控制阀组来控制各个吸气孔的打开和关闭，当所述压缩机只有一个吸气孔时，则设置一个控制阀组；当所述压缩机有多个吸气孔时，一般会对应设置多个控制阀组，这样控制较为繁琐。因 此在本申请的一实施例中，所述第二吸气孔12与所述上止点的距离为L，所述上止点与所述下止点之间的距离为S，其中，0.5S＜L。所述活塞21在运动过程中，所述第一吸气孔11及所述第二吸气孔12的开闭状态如下：
气缸的吸气行程，包括：
第一行程：所述活塞21自所述上止点向所述下止点活动，且距所述上止点的距离小于0.5S。在第一行程中，所述控制阀组开启，使得所述第一吸气孔11导通，且所述第二吸气孔12被所述活塞21遮挡。此时，所述缸体1的工作腔1a仅通过所述第一吸气孔11实现吸气。此时所述工作腔1a内的冷媒总量均来自于所述第一吸气孔11，即第一冷凝回路的冷媒。可以理解的是，由于所述活塞21在向靠近所述下止点的位置活动时，所述缸体1的工作腔1a的压缩空间增大，处于负压状态，便于外部的气流自所述第一吸气孔11进入所述缸体1的工作腔1a。而由于经由所述第一吸气孔11的气流压力小于经由所述第二吸气孔12的气流压力。故，在此活动行程中，通过所述活塞21将所述第二吸气孔12遮挡，以避免所述第二吸气孔12的气流阻碍所述第一吸气孔11的气流进入所述缸体1的工作腔1a。
第二行程：在所述活塞21自所述上止点向所述第下止点活动，且距所述上止点的距离大于0.5S。在第二行程中，所述活塞21未遮挡所述第二吸气孔12，使得所述第二吸气孔12连通所述缸体1的工作腔1a。此时，所述控制阀组按实际需求在开启状态与闭合状态之间切换。在所述控制阀组处于开启状态时，所述第一吸气孔11及所述第二吸气孔12同时向所述缸体1的工作腔1a输入气流。由于在第一行程中，所述缸体1的工作腔1a的空间内经由所述第一吸气孔11吸入了一定量的气流，使得压缩空间中具有一定的气流压力。故，在经由所述第二吸气孔12向所述缸体1的工作腔1a输入气流时，对所述第一吸气孔11的气流影响较小。且由于所述第二吸气孔12到所述上止点的距离大于0.5S，也即到所述第一吸气孔11的距离大于0.5S，使得两者之间存在适宜的缓冲距离，减轻了所述第二吸气孔12的气流对所述第一吸气孔11气流的阻碍影响，提高压缩能效。在所述控制阀组处于闭合状态时，所述第二吸气孔12向所述缸体1的工作腔1a输入气流。此时补充至所述工作腔1a内的冷媒来自于所述第二吸气孔12，即第二冷凝回路的冷媒均回流至所述缸体1的工作腔1a内。可以理解的是，所述第二吸气孔12越靠近所述上止点 与所述下止点的中点，所述第二吸气孔12开启时间早，并且关闭的时间晚，所述第二冷凝回路提供的高压冷媒时间长，补气量大；所述第二吸气孔12越靠近所述下止点时，所述第二吸气孔12开启时间晚，并且关闭的时间早，所述第二冷凝回路提供的高压冷媒时间短，补气时间短，从而补气量也较少。在现实中，可以依据补气量的需求，来设置所述第二吸气孔12的位置。
气缸的压缩行程，包括：
第三行程：所述活塞21自所述下止点向靠近所述上止点的方向活动，且距所述上止点大于0.5S。在第三行程中，所述控制阀组关闭，所述活塞21向靠近所述上止点的方向快速活动。此时，所述第二吸气孔12仍然向所述缸体1的工作腔1a输入气流。此时补充至所述工作腔1a内的冷媒来自于所述第二吸气孔12。因此，在第三行程中，所述缸体1的工作腔1a中的气流被压缩时，尚不会过度阻碍经由所述第二吸气孔12输入所述缸体1的工作腔1a内的气流，使得所述缸体1在压缩行程中，仍可吸入气流。并且，由于所述缸体1的工作腔1a中混合有来自所述第一吸气孔11及所述第二吸气孔12的气流，使得所述缸体1的工作腔1a中气流压力小于经由所述第二吸气孔12内的气流压力。
第四行程：所述活塞21自所述下止点向靠近所述上止点的方向活动，且距所述上止点的距离小于0.5S。在第四行程中，所述控制阀组仍关闭，且所述活塞21遮挡所述第二吸气孔12。此过程中，所述活塞21将所述缸体1的工作腔1a中的气流压缩成高压气流。并在所述活塞21活动至所述下止点时，所述缸体1的工作腔1a中的气流压力压缩到位。此时，连通所述缸体1的工作腔1a的输出管道的控制阀组从关闭状态切换为打开状态，以输出压缩好的高压气流。
所述压缩气缸100对应两个冷凝流路的工作线路为：
第一吸气流道中气流的流路为：所述第一冷凝流路→所述第一吸气孔11→所述缸体1的工作腔1a。
所述第二吸气流道中气流流路为：所述第二冷凝流路→所述第二吸气孔12→所述缸体1的工作腔1a。
且所述压缩气缸100还包括与所述缸体1的工作腔1a连通的内排管，所述内排管用以与排气外管连通，以将所述缸体1的工作腔1a内压缩好的高压 气流自所述内排管排出至排气外管。
在具体现实中，所述第一冷凝流路对应的是冰箱冷冻室，因冷冻室所需的制冷量较大，所需的冷媒量较多，在工作工程中，其消耗掉的冷媒的压力也较多，而所述第二冷凝流路对应的是冰箱冷藏室，因冷藏室所需的制冷量较小，其消耗掉的冷媒的压力也较少，这样回流至所述第一吸气孔11内的压力是远小于所述第二吸气孔12的压力，但是第一冷凝流路的冷媒量较大，这样在所述压缩气缸100工作时，通过所述活塞21先在吸气的前大半段的吸气行程中主要是打开第一吸气孔11进行主吸气，能够吸入冷冻室对应的冷凝流路上的较大的冷媒量，在后面小半段的吸气行程中，所述第二吸气孔12与所述工作腔1a连通，第一吸气孔11关闭，所述第二吸气孔12开始补入高压冷媒气体，并在压缩阶段的前小半段行程继续补气，最后在压缩的后大半段行程中，所述第二吸气孔12关闭，所述活塞21将所述工作腔1a内的冷媒进行压缩，通过设置所述第二吸气孔12距离所述上止点和所述下止点的距离，可以控制所述第二吸气孔12的进气量，即，因所述第二吸气孔12的位置设定，可以使得所述活塞21在往复运动的时候，来调整所述第二吸气孔12开闭的时长，从而实现调节所述第一吸气孔11和所述第二吸气孔12的流量配比。并且通过将所述第二吸气孔12设置于所述缸体1的侧壁上，且靠近下止点设置，从而使得所述压缩气缸100无需专门设置控制阀组来控制所述第二吸气孔12的开闭，而是在所述活塞21的活动行程中就能实现对所述第二吸气孔12的自动开闭，结构设计巧妙，还节约了成本。
需要说明的是，请参阅图5和图6，所述上止点与所述下止点之间的距离为S，即所述上止点是指所述活塞21靠近所述缸体1的气缸盖的一端的端面运动至靠近所述缸体1的底壁的最近的距离时，所述活塞21靠近所述缸体1的底壁的一端所在的位置，所述下止点是指所述活塞21靠近所述缸体1的底壁的一端的端面运动至远离所述缸体1的气缸盖的最远的距离时，所述活塞21靠近所述缸体1的底壁的一端所在的位置。也即距离S为所述活塞21靠近所述缸体1的底壁的一端的端面两种极限状态下之间的距离。所述第二吸气孔12与所述上止点的距离为L，也即，所述第二吸气孔12的中心线与所述上止点的距离为L。
进一步地，请参阅图4和图5，在一实施例中，所述第二吸气孔12位于所述上止点和所述下止点之间，且邻近所述下止点设置，在所述第二吸气孔12邻近所述下止点的时候，相对于将所述第二吸气孔12设置靠近在所述上止点与所述下止点的中点附近来说，当所述活塞21自所述上止点向所述下止点活动的时候，所述第一吸气孔11被打开，与所述第一吸气孔11连通外部高压冷媒气体的第一吸气管输入一定压力P1的高压气体，在所述活塞21刚打开所述第二吸气孔12的瞬间，所述工作腔1a内部的体积V1大于将所述第二吸气孔12设置靠近在所述上止点与所述下止点的中点附近时的所述工作腔1a内部的体积V2，这样当第一吸气孔11吸气工作的时候，缸体1内的压力Pa较小，而所述第二吸气孔12入口的压力P2大于Pa，且压力差ΔPa较大，此刻，所述工作腔1a内的Pa小于临界压力值P0时，在普通直管道中，气体液体流速的极限是当时压力温度条件下的音速，音波的传递速度，代表的是当时压力温度条件下介质可以稳定传导力的极限，流体在接近音速时，密度会大幅减小，这时因流体的体积暴增，会在管道内造成壅塞，从而使流体的速度达不到音速，无论如何加压，气体液体流速都不再提升，当采用所述渐缩孔段12a设计，根据公式：
可以得知，使得气体的流速达到临界流速c
fc，即达到当地音速，此时气体的流速和气压均处于恒定的状态，故，所述第二吸气孔12内的气压处于稳定的临界压力值P0，此刻所述第二吸气孔12进入到所述工作腔1a内的流速为当地音速，所述第二吸气孔12产生的压力和流速均控制在恒定的范围内，所述减缩孔段12a的流量和所述渐缩孔段12a的截面最小直径D相关，在本实施例中，所述渐缩孔段12a的截面最小直径为D1，其中，D1≤3mm，所述第二吸气孔12邻近所述下止点设置时，势必在所述活塞21往复运动的过程中，所述第二吸气孔12处于打开状态的时间较短，这样所述第二吸气孔12的截面最小直径设置得适当大一点，用以调节补气总量，当D1≤3mm时，可以根据需要补气的补气量来调节所述渐缩孔段12a的截面最小直径的同时，保证补气总量部超过所需的补气总量。本实施例的方案适用于补气量较小的压缩机200。
需要说明的是，临界压力P0是指物质处于临界状态时的压力(压强)。 就是在临界温度时使气体液化所需要的最小压力。也就是液体在临界温度时的饱和蒸气压。在临界温度和临界压力下，物质的摩尔体积称为临界摩尔体积。临界温度和临界压力下的状态称为临界状态。对应本申请中，也就是冷媒的饱和蒸气压。
请参阅图6，在另一实施例中，所述第二吸气孔12位于所述上止点和所述下止点之间，且邻近所述上止点与所述下止点的中点设置，此时所述第一吸气孔11被打开，与所述第一吸气孔11连通外部高压冷媒气体的第一吸气管输入一定压力P1的高压气体，在所述活塞21刚打开所述第二吸气孔12的瞬间，所述工作腔1a内部的体积V2小于将所述第二吸气孔12设置靠近所述下止点附近时的所述工作腔1a内部的体积V1，这样当第一吸气孔11吸气工作的时候，缸体1内的压力Pb较大，即Pb＞Pa，而所述第二吸气孔12入口的压力P2大于Pb，且压力差ΔPb较小，即ΔPb＜ΔPa，此刻，所述工作腔1a内的Pb大于临界压力值P0，当Pb＞P0时，也说明此刻所述第二吸气孔12进入到所述工作腔1a内的流速始终是达不到当地音速的。并且因所述第二吸气孔12邻近所述上止点与所述下止点的中点设置时，势必在所述活塞21往复运动的过程中，所述第二吸气孔12处于打开状态的时间较长，这样所述第二吸气孔12的截面最小直径D2设置得适当小一点，用以调节补气总量，为了根据需要补气的补气量来调节所述渐缩孔段12a的截面最小直径的同时，保证补气总量部超过所需的补气总量，在本实施例中，所述渐缩孔段12a的截面最小直径为D2，其中，D2≤2mm。本实施例的方案适用于需要补气量较大的压缩机200。
进一步地，因所述第二吸气孔12开设于压缩机200曲轴箱缸体1孔的壁面，因压缩机200曲轴箱缸体1孔的壁面的厚度与所述渐缩孔段12a的长度并不一定是处于完全匹配的状态，在本实施例中，所述第二吸气孔12还包括与所述渐缩孔段12a的两端分别连通设置的两个直孔段12b，可以通过所述两个直孔段12b进行过渡调节，即当所述渐缩孔段12a需要设置的长度较长的时候，可以将所述两个直孔段12b的长度设置得较短，反之，当所述渐缩孔段12a需要设置的长度较短的时候，可以将所述两个直孔段12b的长度设置得较长。
具体地，在本实施例中，所述第二吸气孔12的截面呈圆形或椭圆形。当 所述第二吸气孔12的截面为圆形时，因内壁面受到的压强相同，这样使得所述第二吸气孔12的受力最均匀，且强度最高。
此外，为实现上述目的，本申请还提出一种压缩机200，所述压缩机200包括上述技术方案所述的压缩气缸100。需要说明的是，所述压缩机200的压缩气缸100的详细结构可参照上述压缩气缸100的实施例，此处不再赘述；由于在本申请的压缩机200中使用了上述压缩气缸100，因此，本申请压缩机200的实施例包括上述压缩气缸100全部实施例的全部技术方案，且所达到的技术效果也完全相同，在此不再赘述。
此外，为实现上述目的，请参阅图7，本申请还提出一种制冷设备，所述制冷设备包括上述技术方案所述的压缩机200。需要说明的是，所述制冷设备的压缩机200的详细结构可参照上述压缩机200的实施例，此处不再赘述；由于在本申请的制冷设备中使用了上述压缩机200，因此，本申请制冷设备的实施例包括上述压缩机200全部实施例的全部技术方案，且所达到的技术效果也完全相同，在此不再赘述。
需要说明的是，所述制冷设备的具体形式不做限制，可以是空调，也可以是新风机，还可以是其他设备。具体地，在本实施例中，所述制冷设备为冰箱。
以上所述仅为本申请的优选实施例，并非因此限制本申请的专利范围，凡是在本申请的发明构思下，利用本申请说明书及附图内容所作的等效结构变换，或直接/间接运用在其他相关的技术领域均包括在本申请的专利保护范围内。
Claims (10)
- 一种压缩气缸，其中，包括：缸体，所述缸体的气缸盖设置有第一吸气孔，且侧壁设置有第二吸气孔；以及，活塞组件，包括活动设于所述缸体内的活塞，所述活塞与所述缸体的底部之间形成工作腔，所述活塞在活动行程中具有位于靠近所述缸体的气缸盖的上止点及远离所述缸体的气缸盖的下止点，所述第二吸气孔位于所述上止点和所述下止点之间；其中，所述第二吸气孔包括渐缩孔段，所述渐缩孔段自所述缸体的外侧向内侧的方向呈渐缩设置。
- 如权利要求1所述的压缩气缸，其中，所述渐缩孔段呈相对设置的两个内壁之间形成的夹角度数为α，其中，50°≤α≤150°。
- 如权利要求1所述的压缩气缸，其中，所述第二吸气孔与所述上止点的距离为L，所述上止点与所述下止点之间的距离为S，其中，0.5S＜L。
- 如权利要求3所述的压缩气缸，其中，所述第二吸气孔邻近所述下止点设置；所述渐缩孔段的截面最小孔径为D1，其中，D1≤3mm。
- 如权利要求3所述的压缩气缸，其中，所述第二吸气孔邻近所述上止点与所述下止点的中点设置；所述渐缩孔段的截面最小孔径为D2，其中，D2≤2mm。
- 如权利要求1所述的压缩气缸，其中，所述第二吸气孔还包括与所述渐缩孔段的两端分别连通设置的两个直孔段。
- 如权利要求1所述的压缩气缸，其中，所述第二吸气孔的截面呈圆形 或椭圆形。
- 一种压缩机，其中，包括如权利要求1至7中任意一项所述的压缩气缸。
- 一种制冷设备，其中，包括如权利要求8所述的压缩机。
- 如权利要求9所述的制冷设备，其中，所述制冷设备为冰箱。
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| CN202220342616.7U CN216812089U (zh) | 2022-02-18 | 2022-02-18 | 压缩气缸、压缩机及制冷设备 |
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