Compressor and refrigeration equipment

Abstract

The invention discloses a compressor and refrigeration equipment, and relates to the technical field of compressors, the compressor comprises a machine shell, a first liquid storage tank, a second liquid storage tank, a first air cylinder and a second air cylinder, the machine shell is provided with an air suction port and an air supply port which are oppositely arranged in the axial direction of the machine shell, and the first liquid storage tank is communicated with the air supply port; the second liquid storage tank is communicated with the air suction port, the second liquid storage tank and the first liquid storage tank are staggered in the circumferential direction of the machine shell, the displacement of the first air cylinder is V1, the displacement of the second air cylinder is V2, and the corresponding central angle theta of the second liquid storage tank and the first liquid storage tank in the circumferential direction of the machine shell and the radius R of the second air inlet hole are set to be V; when the diameter D of the air injection hole is set to meet the following relational expression that 0.2 < = V2 / V1 * (R / D) / theta < = 1.82, the arrangement positions of the first liquid storage tank and the second liquid storage tank are reasonable, the air supply amount can be increased in the air suction and air supply processes, and secondary air suction overheating can be well reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a compressor and a refrigeration device. Background Art

[0002] With the continuous advancement of heat pump technology, people are paying more and more attention to the heating capacity and energy efficiency performance of compressors in low-temperature environments. The heating capacity of traditional compressors tends to drop significantly under low-temperature conditions. The main reason is that the compression ratio increases, which leads to a significant decrease in the volumetric efficiency of the compressor. In addition, the suction density decreases in low-temperature environments, further reducing the suction volume. In order to solve the problems of heating capacity and energy efficiency at low temperatures, jet enthalpy increase technology was introduced to effectively increase the suction volume of the compressor. At the same time, the use of multi-stage compression can avoid the compression ratio of each compression cylinder being too high, thereby improving the volumetric efficiency. However, how to reduce the overheating problem of the secondary suction while increasing the air supply volume is still a challenge that needs to be solved urgently. Summary of the invention

[0003] The main purpose of the present invention is to provide a compressor and a refrigeration device, aiming to solve the problem of how to reduce the superheat of the secondary suction air while increasing the air supply volume of the jet enthalpy increase compressor.

[0004] To achieve the above object, the compressor proposed by the present invention comprises: A casing, wherein an air intake port and an air supply port are provided on the casing, and the air intake port and the air supply port are arranged opposite to each other in the axial direction of the casing; A first liquid storage tank is connected to the gas replenishment port; a second liquid storage tank, connected to the air inlet, wherein the second liquid storage tank and the first liquid storage tank are staggered in the circumferential direction of the housing; A first cylinder is disposed in the housing, the first cylinder includes a first cylinder body, the first cylinder body has a first air inlet hole and a first air outlet hole, the first air inlet hole is connected to the air intake port; and A second cylinder is disposed in the housing, the second cylinder comprises a second cylinder body, the second cylinder body has a second air inlet and a second air outlet, the second air inlet is connected to the first air outlet, the second air outlet is connected to the inner cavity of the housing, and the second cylinder body is further provided with an air injection hole, the air injection hole is connected to the second air inlet and the air supply port; Among them, the displacement of the first cylinder is V1, the displacement of the second cylinder is V2, the radius of the second air inlet hole is R, the diameter of the injection hole is D, the central angle between the second liquid storage tank and the first liquid storage tank in the circumferential direction of the casing is θ, and 0.2≤V2 / V1*(R / D) / θ≤1.82.

[0005] In one embodiment, 0.3≤R / D≤1.67.

[0006] In one embodiment, θ≤90°.

[0007] In one embodiment, the compressor also includes a partition plate arranged between the first cylinder body and the second cylinder body, a buffer groove is arranged on the end surface of the partition plate facing the first cylinder body, and a connecting hole is also arranged on the partition plate, which is connected with the buffer groove and passes through the other end surface thereof, the buffer groove is connected with the first exhaust hole, and the connecting hole is connected with the second intake hole.

[0008] In one embodiment, in a direction away from the partition, the second air inlet hole is inclined toward a middle portion of the second cylinder body.

[0009] In one embodiment, a cross-sectional area of ​​the second air inlet hole is S1, a cross-sectional area of ​​the connecting hole is S2, and 0.2≤S2 / S1≤1.2.

[0010] In one embodiment, the inner side wall of the first cylinder body is provided with a first slide groove, and the first cylinder further comprises: A first sliding sheet is disposed in the first sliding groove; and A first rolling piston; The inner side wall of the second cylinder body is provided with a second slide groove, and the second cylinder further comprises: A second sliding plate is telescopically installed in the second sliding groove along the radial direction of the second cylinder body; and a second rolling piston; Wherein, the first sliding plate and the second sliding plate are arranged opposite to each other in the axial direction of the housing.

[0011] In one embodiment, a connecting groove is formed in the outer peripheral wall of the second rolling piston; A connecting column is disposed at the end of the second sliding sheet, and the connecting column is rotatably matched with the connecting groove.

[0012] The present invention also provides a refrigeration device, the refrigeration device comprises a compressor, and the compressor comprises: A casing, wherein an air intake port and an air supply port are provided on the casing, and the air intake port and the air supply port are arranged opposite to each other in the axial direction of the casing; A first liquid storage tank is connected to the gas replenishment port; a second liquid storage tank, connected to the air inlet, wherein the second liquid storage tank and the first liquid storage tank are staggered in the circumferential direction of the housing; A first cylinder is disposed in the housing, the first cylinder includes a first cylinder body, the first cylinder body has a first air inlet hole and a first air outlet hole, the first air inlet hole is connected to the air intake port; and A second cylinder is disposed in the housing, the second cylinder comprises a second cylinder body, the second cylinder body has a second air inlet and a second air outlet, the second air inlet is connected to the first air outlet, the second air outlet is connected to the inner cavity of the housing, and the second cylinder body is further provided with an air injection hole, the air injection hole is connected to the second air inlet and the air supply port; Among them, the displacement of the first cylinder is V1, the displacement of the second cylinder is V2, the radius of the second air inlet hole is R, the diameter of the injection hole is D, the central angle between the second liquid storage tank and the first liquid storage tank in the circumferential direction of the casing is θ, and 0.2≤V2 / V1*(R / D) / θ≤1.82.

[0013] In one embodiment, the refrigeration device comprises a heat pump.

[0014] In the technical solution of the present invention, the casing is provided with an air intake port and an air supply port which are connected to the inner cavity of the casing and are arranged opposite to each other in the axial direction of the casing. The second liquid storage tank is connected to the first air intake hole of the first cylinder through the air intake port. The first cylinder discharges the compressed refrigerant to the second air intake hole of the second cylinder body of the second cylinder through the first exhaust hole arranged on the first cylinder body. The second cylinder body is also provided with an injection hole which is connected to the second air intake hole and the air supply port. The first liquid storage tank is connected to the first air intake hole through the injection hole through the air supply port. The injection hole of the second cylinder replenishes air. Since the second liquid storage tank and the first liquid storage tank are staggered in the circumferential direction of the casing, the central angle θ corresponding to the second liquid storage tank and the first liquid storage tank in the circumferential direction of the casing, and the radius R of the second air inlet hole, the diameter D of the injection hole are set to satisfy the following relationship: 0.2≤V2 / V1*(R / D) / θ≤1.82. The positions of the first liquid storage tank and the second liquid storage tank are reasonably arranged, which can not only increase the air replenishment amount during the air intake and air replenishment process, but also well reduce the secondary air intake overheating. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the structures shown in these drawings without paying creative work.

[0016] Figure 1A schematic structural diagram of an embodiment of a compressor provided by the present invention; Figure 2 for Figure 1 A top view of the compressor; Figure 3 for Figure 1 A cross-sectional view of the compressor; Figure 4 for Figure 3 Cross-sectional view of AA in the middle; Figure 5 A linear diagram of the performance of the compressor provided by the present invention.

[0017] Description of Figure Numbers: 100. Compressor; 1. Casing; a. Air intake; b. Air supply; 2. First liquid storage tank; 3. Second liquid storage tank; 4. First cylinder; 41. First cylinder body; c. First working chamber; d. First air inlet; e. First air outlet; 42. First rolling piston; 5. Second cylinder; 51. Second cylinder body; 51a. Second slide groove; f. Second working chamber; g. Second air inlet; k. Air injection hole; 52. Second slide vane; 53. Second rolling piston; 6. Partition; m. Buffer groove; n. Connecting hole.

[0018] The realization of the purpose, functional features and advantages of the present invention will be further explained in conjunction with embodiments and with reference to the accompanying drawings. DETAILED DESCRIPTION

[0019] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0020] It should be noted that if the embodiments of the present invention involve directional indications (such as up, down, left, right, front, back, etc.), the directional indications are only used to explain the relative position relationship, movement status, etc. between the components in a certain specific posture. If the specific posture changes, the directional indication will also change accordingly.

[0021] In addition, if there are descriptions involving "first", "second", etc. in the embodiments of the present invention, the descriptions of "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the number of technical features indicated. Therefore, the features limited to "first" and "second" may explicitly or implicitly include at least one of the features. In addition, if "and / or" or "and / or" appears in the full text, its meaning includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, solution B, or solutions that satisfy both A and B. In addition, the technical solutions between the various embodiments can be combined with each other, but it must be based on the ability of ordinary technicians in this field to implement. When the combination of technical solutions is contradictory or cannot be implemented, it should be deemed that such combination of technical solutions does not exist and is not within the scope of protection required by the present invention.

[0022] With the continuous advancement of heat pump technology, people are paying more and more attention to the heating capacity and energy efficiency performance of compressors in low-temperature environments. The heating capacity of traditional compressors tends to drop significantly under low-temperature conditions. The main reason is that the compression ratio increases, which leads to a significant decrease in the volumetric efficiency of the compressor. In addition, the suction density decreases in low-temperature environments, further reducing the suction volume. In order to solve the problems of heating capacity and energy efficiency at low temperatures, jet enthalpy increase technology was introduced to effectively increase the suction volume of the compressor. At the same time, the use of multi-stage compression can avoid the compression ratio of each compression cylinder being too high, thereby improving the volumetric efficiency. However, how to reduce the overheating problem of the secondary suction while increasing the air supply volume is still a challenge that needs to be solved urgently.

[0023] The present invention proposes a compressor 100, which aims to solve the problem of how to reduce the overheating of the secondary suction while increasing the air supply volume in an injection enthalpy increase compressor.

[0024] See also Figures 1 to 3In one embodiment of the present invention, the compressor 100 includes a casing 1, a first liquid storage tank 2, a second liquid storage tank 3, a first cylinder 4 and a second cylinder 5. The casing 1 has a mounting cavity, and an air intake port a and an air supply port b connected to the mounting cavity are provided on the casing 1, and the air intake port a and the air supply port b are arranged opposite to each other in the axial direction of the casing 1; the first liquid storage tank 2 is connected to the air supply port b; the second liquid storage tank 3 is connected to the air intake port a, and the second liquid storage tank 3 and the first liquid storage tank 2 are staggered in the circumferential direction of the casing 1; the first cylinder 4 is arranged in the casing 1, and the first cylinder 4 includes a first cylinder body 41, and the first cylinder body 41 has a first working chamber c, and a first air inlet hole d and a first exhaust hole e connected to the first working chamber c, and the first air inlet hole d is connected to the The air intake port a is connected; the second cylinder 5 is arranged in the casing 1, and the second cylinder 5 includes a second cylinder body 51, the second cylinder body 51 has a second working chamber f, and a second air inlet g and a second exhaust hole connected to the second working chamber f, the second air inlet g is connected to the first exhaust hole e, and the second exhaust hole is connected to the mounting chamber, and the second cylinder body 51 is also provided with an injection hole k, and the injection hole k connects the second air inlet hole g and the air supply port b; wherein, the displacement of the first cylinder 4 is V1, the displacement of the second cylinder 5 is V2, the radius of the second air inlet hole g is R, the diameter of the injection hole k is D, and the central angle corresponding to the second liquid storage tank 3 and the first liquid storage tank 2 in the circumferential direction of the casing 1 is θ, 0.2≤V2 / V1*(R / D) / θ≤1.82.

[0025] It can be understood that the housing 1 is the outer shell of the compressor 100, and the installation cavity is provided inside the housing 1. The air intake port a and the air supply port b are holes opened on the housing 1, which are connected to the installation cavity and are used for air intake and air supply respectively. They are arranged opposite to each other in the axial direction of the housing 1 to facilitate the inflow and outflow of gas.

[0026] The first liquid storage tank 2 is connected to the gas replenishment port b for replenishing gas. The second liquid storage tank 3 is connected to the air inlet a for storing the inhaled gas.

[0027] The compression assembly includes at least two compression assemblies to form a two-stage compressor 100. The first cylinder 4 is located inside the casing 1, including a first cylinder body 41, having the first working chamber c, the air inlet hole and the exhaust hole. The first air inlet hole d is directly connected to the air intake port a and is responsible for inhaling gas. The second cylinder 5 is also located inside the casing 1, including a second cylinder body 51, having the second working chamber f, the air inlet hole and the exhaust hole. The second air inlet hole g is connected to the first exhaust hole e, so that the gas after the first-stage compression will enter the second-stage compression. The injection hole k is located on the second cylinder body 51, connecting the second air inlet hole g and the air supply port b, and is used to cool the gas during the second-stage compression process, reduce gas expansion loss, improve energy efficiency, and improve the efficiency of the second-stage compression.

[0028] It should be noted that the displacement ratio between the displacement V2 of the second cylinder 5 and the displacement V1 of the first cylinder 4 represents the matching degree between the two compression stages. A reasonable displacement ratio can ensure that the exhaust gas of the first cylinder 4 can be effectively supplied to the second cylinder 5, thereby ensuring the flow balance and stability of the entire compression system.

[0029] If the displacement of the second cylinder 5 is too large and the displacement of the first cylinder 4 is too small, the gas sucked into the second cylinder 5 is insufficient, thereby affecting its working efficiency and compression performance.

[0030] If the displacement of the second cylinder 5 is too small, the gas may be retained inside the compression cylinder, resulting in local overheating; otherwise, it may cause poor gas flow, affecting the normal operation of the compressor 100. Therefore, the displacement ratio of the first and second cylinders 5 needs to be comprehensively considered.

[0031] If the displacement of the second cylinder 5 is appropriate, it can ensure that sufficient refrigerant and gas enter, thereby absorbing part of the heat during the compression process and slowing down the temperature rise. It can also ensure that the gas discharged from the first cylinder 4 is fully mixed with the injected refrigerant, further reducing the gas temperature in the second cylinder 5 and reducing overheating.

[0032] It should also be noted that the ratio of the radius R of the second air inlet g to the diameter D of the jet hole k characterizes the flow characteristics of the fluid in the process of entering the second cylinder 5. Because the size (radius and diameter) of the second air inlet g and the jet hole k will directly affect the speed and flow rate of the gas flow. The larger air inlet and the jet hole k can provide a larger flow rate, thereby ensuring that the second cylinder 5 can effectively inhale enough gas and refrigerant to ensure the smooth progress of the compression process. If the radius of the second air inlet g is too small relative to the diameter of the jet hole k, it may cause greater flow resistance and pressure loss, thereby reducing the amount of gas entering the second cylinder 5, which may lead to insufficient suction and reduced compression efficiency.

[0033] Because the refrigerant injected into the injection hole k can absorb part of the heat during the compression process, the increase in gas temperature is suppressed and the superheat is reduced. Therefore, a reasonable design of the diameter ratio of the two can effectively control the temperature in the secondary compression chamber and keep it within a suitable range. The appropriate aperture ratio helps to mix the gas with the injected refrigerant well, ensuring that the gas entering the second cylinder 5 is uniform and avoiding hot spots caused by local overheating.

[0034] It should be noted that when the first liquid storage tank 2 and the second liquid storage tank 3 are installed on the casing 1, if the first liquid storage tank 2 is connected to the air supply port b and they overlap in the axial direction of the casing 1, then the second liquid storage tank 3 must be installed staggered with the first liquid storage tank 2 to avoid interference, and the second liquid storage tank 3 needs to be connected to the air intake port a through a connecting pipe; if the second liquid storage tank 3 is connected to the air intake port a and they overlap in the axial direction of the casing 1, then the first liquid storage tank 2 must be installed staggered with the second liquid storage tank 3 to avoid interference, and the first liquid storage tank 2 needs to be connected to the air supply port b through a connecting pipe.

[0035] Whether the second liquid storage tank 3 or the first liquid storage tank 2 is connected to the casing 1 through a connecting pipe, the connecting pipe needs to be bent and have a certain length to achieve connection. However, when the gas passes through the connecting pipe, it will cause poor gas flow, consume more energy, reduce the suction volume, and reduce the suction efficiency. During the suction process, if the pressure loss of the connecting pipe is too large, it will affect the gas pressure at the inlet of the compressor 100, thereby limiting the amount of gas entering the compressor 100, and further affecting the overall performance and suction volume of the compressor 100. Therefore, the larger the central angle θ corresponding to the second liquid storage tank 3 and the first liquid storage tank 2 in the circumferential direction of the casing 1, the longer the connecting pipe, the greater the pressure loss, and the influence of the suction volume increases accordingly. Therefore, the central angle θ is related to the suction volume.

[0036] In the technical solution of the present invention, the casing 1 is provided with an air intake port a and an air supply port b which are connected to the installation cavity and are arranged opposite to each other in the axial direction of the casing 1. The second liquid storage tank 3 is connected with the first air inlet d of the first cylinder 4 through the air intake port a. The first cylinder 4 discharges the compressed refrigerant to the second air inlet g of the second cylinder body 51 of the second cylinder 5 through the first exhaust port e arranged on the first cylinder body 41. The second cylinder body 51 is also provided with an injection hole k which is connected with the second air inlet g and the air supply port b. The first liquid storage tank 2 is connected with the first air inlet d of the first cylinder 4 through the air intake port b. The jet hole k replenishes air to the jet hole k of the second cylinder 5. Since the second liquid storage tank 3 and the first liquid storage tank 2 are staggered in the circumferential direction of the casing 1, the central angle θ corresponding to the second liquid storage tank 3 and the first liquid storage tank 2 in the circumferential direction of the casing 1, and the radius R of the second air inlet hole g, the diameter D of the jet hole k is set to satisfy the following relationship: 0.2≤V2 / V1*(R / D) / θ≤1.82. The positions of the first liquid storage tank 2 and the second liquid storage tank 3 are reasonably arranged, which can not only increase the air replenishment amount during the air intake and air replenishment process, but also well reduce the secondary air intake overheating.

[0037] See also Figure 5 , Figure 5 A linear diagram of the performance of the compressor provided by the present invention, according to Figure 5 Shown is a performance curve of the compressor 100 when V2 / V1*(R / D) / θ of the compressor 100 is at different values. When 0.2≤V2 / V1*(R / D) / θ≤1.82, the performance of the compressor 100 is at an optimal state.

[0038] Specifically, in this embodiment, 0.3≤R / D≤1.67.

[0039] It should be noted that when R / D is greater than 1.67, it means that the radius of the second air inlet g is too large relative to the diameter of the jet hole k, then the air intake of the second cylinder 5 is relatively large, and the air supply of the jet hole k is relatively small. The amount of gas inhaled by the second cylinder 5 cannot effectively exchange heat with the low-temperature refrigerant added, resulting in an increase in gas temperature and an increase in the risk of overheating of the system. In addition, the amount of low-temperature refrigerant is insufficient and the gas temperature cannot be effectively reduced, thereby reducing the energy conversion efficiency of the gas during the compression process. Overheating of the gas may cause the specific power of the compressor 100 to increase and the overall energy efficiency to decrease.

[0040] When R / D is less than 0.3, it means that the radius of the second air inlet g is too small relative to the diameter of the jet hole k, so the air intake of the second cylinder 5 is relatively small, and the air supply of the jet hole k is relatively large. If the air intake is insufficient and the air supply is too large, the refrigeration capacity of the refrigeration system will be greater than the load demand, resulting in uneven refrigeration effect, some areas will be overcooled while the temperature of other areas cannot reach the set value, and the refrigeration capacity of the entire system will still not meet the design requirements, resulting in the product temperature not meeting the demand.

[0041] Insufficient suction volume causes the compressor 100 to operate under non-optimal working conditions, thereby reducing the overall energy efficiency ratio (COP). Even if a large amount of low-temperature refrigerant is added, the overall efficiency will still be affected if the gas is not fully compressed and utilized.

[0042] In this way, 0.3≤R / D≤1.67 is set, ensuring that the compressor 100 operates in the optimal working state, improving the compression efficiency, thereby increasing the energy efficiency ratio (EER or COP) of the system, while reducing the retention and resistance of the refrigerant in the pipeline, improving the overall heat exchange efficiency, and effectively controlling the intake temperature of the compressor 100 to prevent overheating or overcooling, thereby improving the stability and reliability of the system.

[0043] For further information, see Figure 2 , in this embodiment, θ≤90°.

[0044] In this way, the corresponding central angle θ of the second liquid storage tank 3 and the first liquid storage tank 2 in the circumferential direction of the casing 1 is set to be less than or equal to 90°, so that the second liquid storage tank 3 or the first liquid storage tank 2 can be connected to the casing 1 by reasonably setting the length of the connecting pipe and the bending angle, so that the refrigerant gas replenishment amount can reach a more reasonable level.

[0045] Specifically, see Figure 3 In this embodiment, the compressor 100 also includes a partition plate 6 arranged between the first cylinder body 41 and the second cylinder body 51, and a buffer groove m is arranged on the end surface of the partition plate 6 facing the first cylinder body 41, and a connecting hole n is also arranged on the partition plate 6, which is connected with the buffer groove m and passes through the other end surface thereof, the buffer groove m is connected with the first exhaust hole e, and the connecting hole n is connected with the second intake hole g.

[0046] It is understandable that the buffer groove m is provided on one side of the partition plate 6 (the end surface facing the first cylinder body 41). The buffer groove m is convenient for adjusting the pressure or flow.

[0047] The buffer groove m is connected with the first exhaust hole e, and the gas exhausted from the first cylinder 41 can flow into the buffer groove m. The connecting hole n is connected with the second air inlet hole g, and the gas in the buffer groove m flows to the second cylinder 51 through the connecting hole n.

[0048] Effective regulation and control of the gas is achieved through the partition 6, the buffer groove m and the connecting hole n, which helps to improve the efficiency of the compressor 100 and avoid pressure fluctuations caused by the instantaneous flow of gas. The existence of the buffer groove m can absorb some vibrations or shocks generated during the flow of gas, thereby protecting other components of the compressor 100. Through reasonable airflow design, the gas flow balance between the first cylinder body 41 and the second cylinder body 51 is ensured to improve the overall performance.

[0049] For further information, please refer to Figure 3 In this embodiment, in the direction away from the partition plate 6, the second air inlet g is inclined toward the middle of the second cylinder body 51.

[0050] By arranging the second air inlet g at an angle, the second air inlet g can better guide the gas flow, reduce the air flow resistance, and enhance the fluidity and entry efficiency of the gas. The gas is evenly distributed to the middle of the second cylinder body 51, the filling efficiency of the cylinder is improved, and the full utilization of the gas in each working cycle is ensured. The inclined air inlet can reduce the vortex effect in the air flow and reduce the disturbance when the gas enters the cylinder, thereby improving the overall stability and performance of the compressor 100.

[0051] For further information, see Figure 4 In this embodiment, the cross-sectional area of ​​the second air inlet g is S1, the cross-sectional area of ​​the connecting hole n is S2, and 0.2≤S2 / S1≤1.2.

[0052] The cross-sectional area (S1) of the second air inlet g refers to the area of ​​the second air inlet g perpendicular to the airflow direction, and represents the size of the airflow channel.

[0053] The cross-sectional area (S2) of the communicating hole n refers to the cross-sectional area of ​​the communicating hole n, indicating the ability of gas to pass through the communicating hole n.

[0054] The ratio of the cross-sectional area S2 of the connecting hole n to the cross-sectional area S1 of the second air inlet hole g is set to be greater than or equal to 0.2 and less than or equal to 1.2 to prevent the flow from being too fast or too slow.

[0055] If S2 is too small (for example, S2 / S1<0.2), the resistance of the airflow entering the connecting hole n increases, thereby affecting the filling efficiency of the second cylinder 51 .

[0056] If S2 is too large (for example, S2 / S1>1.2), the gas flow will be uneven, resulting in pressure fluctuations and reduced efficiency.

[0057] An appropriate area ratio helps to ensure that the gas does not experience excessive eddy current or loss when passing through the communication holes n, thereby improving the efficiency of the entire compressor 100 .

[0058] Specifically, see Figure 3 and Figure 4 In this embodiment, the first cylinder body 41 further comprises a first slide groove which is connected to the first working chamber c and extends along the radial direction of the first cylinder body 41, the first cylinder 4 further comprises a first slide and a first rolling piston 42, the first slide is telescopically installed in the first slide groove along the radial direction of the first cylinder body 41; the first rolling piston 42 is used to be driven by the crankshaft to swing eccentrically in the first compression chamber to drive the first slide to move during its swing stroke; the second cylinder body 51 further comprises a second slide groove 51a which is connected to the second working chamber f and extends along the radial direction of the second cylinder body 51, the second cylinder 5 further comprises a second slide 52 and a second rolling piston 53, the second slide 52 is telescopically installed in the second slide groove 51a along the radial direction of the second cylinder body 51; the second rolling piston 53 is used to be driven by the crankshaft to swing eccentrically in the second compression chamber to drive the second slide 52 to move during its swing stroke; wherein, the first slide and the second slide 52 are arranged opposite to each other in the axial direction of the housing 1.

[0059] It should be noted that in order to optimize the working efficiency and performance of the compressor 100 and ensure that when one compression cylinder of the two compression components is exhausting, the other compression cylinder can inhale, and the coordinated cooperation can achieve a smoother airflow and pressure change and reduce pulsation, the slide vanes of the first cylinder 4 and the second cylinder 5 can be arranged to be relatively arranged in the axial direction of the casing 1. When the crankshaft rotates, the two eccentric parts respectively drive the corresponding rolling pistons to drive the slide vanes to move in opposite directions along the radial direction of the cylinder, thereby realizing synchronous intake and exhaust, and effectively reducing the pressure fluctuations caused by the asynchronous operation between the compression cylinders.

[0060] Accordingly, since the first slide and the second slide 52 are arranged opposite to each other in the axial direction of the housing 1, once the position of the slide is determined, the position of the air inlet of the corresponding cylinder can be basically determined, that is, the extension direction of the first air inlet hole d of the first cylinder body 41 and the extension direction of the air injection hole k of the second cylinder body 51 are also arranged opposite to each other in the axial direction of the housing 1. In this way, when the first cylinder 4 and the second cylinder 5 inhale air, the airflow can smoothly flow into the corresponding cylinder along the radial direction of the housing 1.

[0061] Furthermore, in other embodiments, a connecting groove is recessed on the outer peripheral wall of the second rolling piston 53; the second slide plate 52 has a connecting column close to the second rolling piston 53 and cooperating with the connecting groove, so that the second rolling piston 53 can swing around the connecting column of the second slide plate 52.

[0062] When the second rolling piston 53 swings eccentrically in the second working chamber f, the cooperation between the connecting column of the second slide 52 and the connecting groove ensures that the second rolling piston 53 can swing around the connecting column of the second slide 52, and the second slide 52 can move freely in the radial direction, thereby forming a variable compression chamber to achieve gas suction, compression and discharge. The connecting groove and the connecting column of the second slide 52 are always in surface contact, which reduces the possibility of gas leakage from the exhaust side to the intake side, thereby greatly improving the operating efficiency of the compressor 100.

[0063] The present invention also proposes a refrigeration device, which may be an air conditioner or a refrigerator, etc. The refrigeration device includes a heat exchanger and a compressor 100. The specific structure of the compressor 100 refers to the above embodiment. Since the refrigeration device adopts all the technical solutions of all the above embodiments, it has at least all the beneficial effects brought by the technical solutions of the above embodiments, which will not be described one by one here.

[0064] Specifically, in this embodiment, the refrigeration device includes a heat pump. A heat pump is a device that can transfer heat energy between different environments. Its basic principle is to use a refrigeration cycle to transfer heat from a low-temperature area to a high-temperature area. The heat pump uses the above-mentioned two-stage compressor 100 to increase the air supply volume while reducing the superheat of the secondary suction air.

[0065] The above description is only an exemplary embodiment of the present invention, and does not limit the patent scope of the present invention. All equivalent structural changes made by using the contents of the present invention specification and drawings under the technical concept of the present invention, or directly / indirectly applied in other related technical fields are included in the patent protection scope of the present invention.

Claims

1. A compressor, characterized in that: include: A casing, wherein an air intake port and an air supply port are provided on the casing, and the air intake port and the air supply port are arranged opposite to each other in the axial direction of the casing; A first liquid storage tank is connected to the gas replenishment port; a second liquid storage tank, connected to the air inlet, wherein the second liquid storage tank and the first liquid storage tank are staggered in the circumferential direction of the housing; A first cylinder is disposed in the housing, the first cylinder includes a first cylinder body, the first cylinder body has a first air inlet hole and a first air outlet hole, the first air inlet hole is connected to the air intake port; and A second cylinder is disposed in the housing, the second cylinder comprises a second cylinder body, the second cylinder body has a second air inlet and a second air outlet, the second air inlet is connected to the first air outlet, the second air outlet is connected to the inner cavity of the housing, and the second cylinder body is further provided with an air injection hole, the air injection hole is connected to the second air inlet and the air supply port; Among them, the displacement of the first cylinder is V1, the displacement of the second cylinder is V2, the radius of the second air inlet hole is R, the diameter of the injection hole is D, the central angle between the second liquid storage tank and the first liquid storage tank in the circumferential direction of the casing is θ, and 0.2≤V2 / V1*(R / D) / θ≤1.

82.

2. The compressor according to claim 1, characterized in that 0.3≤R / D≤1.

67.

3. The compressor according to claim 1, characterized in that θ≤90°.

4. The compressor according to claim 1, characterized in that The compressor also includes a partition plate arranged between the first cylinder body and the second cylinder body, a buffer groove is arranged on the end surface of the partition plate facing the first cylinder body, and a connecting hole is also arranged on the partition plate, which is connected with the buffer groove and passes through the other end surface thereof, the buffer groove is connected with the first exhaust hole, and the connecting hole is connected with the second intake hole.

5. The compressor according to claim 4, characterized in that In a direction away from the partition, the second air inlet hole is inclined toward a middle portion of the second cylinder body.

6. The compressor according to claim 4 or 5, characterized in that: The cross-sectional area of ​​the second air inlet hole is S1, the cross-sectional area of ​​the connecting hole is S2, and 0.2≤S2 / S1≤1.

2.

7. The compressor according to claim 1, characterized in that The inner side wall of the first cylinder body is provided with a first slide groove, and the first cylinder further comprises: A first sliding sheet is disposed in the first sliding groove; and A first rolling piston; The inner side wall of the second cylinder body is provided with a second slide groove, and the second cylinder further comprises: A second sliding sheet is disposed in the second sliding groove; and a second rolling piston; Wherein, the first sliding plate and the second sliding plate are arranged opposite to each other in the axial direction of the housing.

8. The compressor according to claim 7, characterized in that The outer peripheral wall of the second rolling piston is concavely provided with a connecting groove; A connecting column is disposed at the end of the second sliding sheet, and the connecting column is rotatably matched with the connecting groove.

9. A refrigeration device, characterized in that: Comprising a compressor as claimed in any one of claims 1 to 8.

10. The refrigeration device according to claim 9, characterized in that: The refrigeration equipment comprises a heat pump.

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