Compressor and Refrigeration Equipment

Abstract

The present invention discloses a compressor and a refrigeration device, relating to the technical field of compressors. Among them, the compressor includes a housing, a first liquid storage tank, a second liquid storage tank, a first cylinder and a second cylinder. An air inlet and a gas supplement port are provided on the housing and are oppositely arranged in its axial direction. The first liquid storage tank is communicated with the gas supplement port; the second liquid storage tank is communicated with the air inlet, and the second liquid storage tank and the first liquid storage tank are staggeredly arranged in the circumferential direction of the housing. The displacement of the first cylinder is V1, and the displacement of the second cylinder is V2. When the central angle θ corresponding to the second liquid storage tank and the first liquid storage tank in the circumferential direction of the housing, the radius R of the second air inlet hole, and the diameter D of the air injection hole are set to satisfy the following relational expression: 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, and it can not only increase the gas supplement amount during the air intake and gas supplement processes, but also well reduce the superheat of the secondary air intake.

Description

Technical Field

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

[0002] With the continuous progress of heat pump technology, people have paid increasing attention to the heating capacity and energy efficiency performance of compressors in low-temperature environments. For traditional compressors under low-temperature conditions, their heating capacity often significantly decreases. The main reason is that the increase in compression ratio leads to a significant decrease in the volumetric efficiency of the compressor. In addition, the suction density decreases in a low-temperature environment, further reducing the suction volume. To solve the problems of heating capacity and energy efficiency at low temperatures, the jet injection enthalpy increase technology is introduced to effectively increase the suction volume of the compressor. At the same time, the multi-stage compression method can avoid too high a compression ratio for each compression cylinder, thereby improving the volumetric efficiency. However, how to reduce the superheat problem of the secondary suction while increasing the gas supplement volume remains an urgent challenge to be solved. Summary of the Invention

[0003] The main object of the present invention is to propose a compressor and a refrigeration device, aiming to solve the problem of how to reduce the superheat of the secondary suction while increasing the gas supplement volume in a jet injection enthalpy increase compressor.

[0004] To achieve the above object, the compressor proposed by the present invention includes:

[0005] A housing, on which an air suction port and a gas supplement port are provided, and the air suction port and the gas supplement port are oppositely arranged in the axial direction of the housing;

[0006] A first liquid storage tank, which is communicated with the gas supplement port;

[0007] A second liquid storage tank, which is communicated with the air suction port, and the second liquid storage tank and the first liquid storage tank are staggeredly arranged in the circumferential direction of the housing;

[0008] A first cylinder, which is arranged in the housing, the first cylinder includes a first cylinder block, the first cylinder block has a first intake hole and a first exhaust hole, and the first intake hole is communicated with the air suction port; and,

[0009] A second cylinder, which is arranged in the housing, the second cylinder includes a second cylinder block, the second cylinder block has a second intake hole and a second exhaust hole, the second intake hole is communicated with the first exhaust hole, the second exhaust hole is communicated with the inner cavity of the housing, and a jet hole is further provided on the second cylinder block, and the jet hole communicates the second intake hole and the gas supplement port;

[0010] Among them, the displacement of the first cylinder is V1, the displacement of the second cylinder is V2, the radius of the second intake hole is R, the diameter of the injection hole is D, and the central angle corresponding to the second liquid storage tank and the first liquid storage tank in the circumferential direction of the casing is θ, where 0.2 ≤ V2 / V1 * (R / D) / θ ≤ 1.82.

[0011] In one embodiment, 0.3 ≤ R / D ≤ 1.67.

[0012] In one embodiment, θ ≤ 90°.

[0013] In one embodiment, the compressor further includes a partition plate disposed between the first cylinder block and the second cylinder block. A buffer groove is provided on the end surface of the partition plate facing the first cylinder block, and a communication hole communicating with the buffer groove and penetrating through the other end surface is further provided on the partition plate. The buffer groove communicates with the first exhaust hole, and the communication hole communicates with the second intake hole.

[0014] In one embodiment, in the direction away from the partition plate, the second intake hole is inclined towards the middle of the second cylinder block.

[0015] In one embodiment, the cross-sectional area of the second intake hole is S1, the cross-sectional area of the communication hole is S2, and 0.2 ≤ S2 / S1 ≤ 1.2.

[0016] In one embodiment, a first sliding groove is provided on the inner side wall of the first cylinder block. The first cylinder further includes:

[0017] A first sliding piece disposed in the first sliding groove; and,

[0018] A first rolling piston;

[0019] A second sliding groove is provided on the inner side wall of the second cylinder block. The second cylinder further includes:

[0020] A second sliding piece slidably mounted in the second sliding groove along the radial direction of the second cylinder block; and,

[0021] A second rolling piston;

[0022] Among them, the first sliding piece and the second sliding piece are oppositely arranged in the axial direction of the casing.

[0023] In one embodiment, a connecting groove is recessed on the outer peripheral wall of the second rolling piston;

[0024] A connecting column is provided at the end of the second sliding piece, and the connecting column is rotatably matched with the connecting groove.

[0025] The present invention also provides a refrigeration device, which includes a compressor. The compressor includes:

[0026] A housing on which an air suction port and a gas supplement port are formed. The air suction port and the gas supplement port are oppositely arranged in the axial direction of the housing;

[0027] A first liquid storage tank communicated with the gas supplement port;

[0028] A second liquid storage tank communicated with the air suction port. The second liquid storage tank and the first liquid storage tank are staggeredly arranged in the circumferential direction of the housing;

[0029] A first cylinder disposed inside the housing. The first cylinder includes a first cylinder block having a first air inlet hole and a first air outlet hole. The first air inlet hole is communicated with the air suction port; and,

[0030] A second cylinder disposed inside the housing. The second cylinder includes a second cylinder block having a second air inlet hole and a second air outlet hole. The second air inlet hole is communicated with the first air outlet hole. The second air outlet hole is communicated with the inner cavity of the housing. A gas injection hole is further formed on the second cylinder block, and the gas injection hole communicates the second air inlet hole and the gas supplement port;

[0031] Wherein, 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 gas injection hole is D, and the central angle corresponding to the second liquid storage tank and the first liquid storage tank in the circumferential direction of the housing is θ, and 0.2 ≤ V2 / V1 * (R / D) / θ ≤ 1.82.

[0032] In an embodiment, the refrigeration device includes a heat pump.

[0033] In the technical solution of the present invention, an air inlet and a gas supplementing port are provided on the casing, which are communicated with the inner cavity of the casing and are oppositely arranged in the axial direction of the casing. The second liquid storage tank is communicated with the first air inlet hole of the first cylinder through the air inlet. The first cylinder discharges the compressed refrigerant to the second air inlet hole of the second cylinder body of the second cylinder through the first exhaust hole provided on the first cylinder body. A gas injection hole communicating the second air inlet hole and the gas supplementing port is further provided on the second cylinder body. The first liquid storage tank supplements gas to the gas injection hole of the second cylinder through the gas supplementing port and the gas injection hole. Since the second liquid storage tank and the first liquid storage tank are staggeredly arranged 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, the radius R of the second air inlet hole, and the diameter D of the gas injection hole are set to satisfy the following relational expression: when 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, and the gas supplementing amount can be increased during the air intake and gas supplementing processes, and the secondary intake superheat can be well reduced. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] In order to more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on the structures shown in these drawings without creative efforts.

[0035] Figure 1 is a schematic structural diagram of an embodiment of a compressor provided by the present invention;

[0036] Figure 2 is Figure 1 the top view of the compressor in;

[0037] Figure 3 is Figure 1 the sectional view of the compressor in;

[0038] Figure 4 is Figure 3 the sectional view taken along A-A in;

[0039] Figure 5 is a linear diagram of the performance of the compressor provided by the present invention.

[0040] Description of the reference numerals in the drawings:

[0041] 100. Compressor; 1. Housing; a. Suction port; b. Gas supplement port; 2. First liquid storage tank; 3. Second liquid storage tank; 4. First cylinder; 41. First cylinder block; c. First working chamber; d. First intake hole; e. First exhaust hole; 42. First rolling piston; 5. Second cylinder; 51. Second cylinder block; 51a. Second chute; f. Second working chamber; g. Second intake hole; k. Jet hole; 52. Second sliding vane; 53. Second rolling piston; 6. Partition; m. Buffer groove; n. Communication hole.

[0042] The realization, functional features and advantages of the object of the present invention will be further described with reference to the embodiments and the accompanying drawings. Specific embodiments

[0043] The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all embodiments. All other embodiments obtained by those of ordinary skill in the art based on the embodiments of the present invention without creative efforts shall fall within the protection scope of the present invention.

[0044] It should be noted that if there are directional indications (such as up, down, left, right, front, back...) in the embodiments of the present invention, the directional indications are only used to explain the relative position relationship and movement conditions between components in a specific posture. If the specific posture changes, the directional indications will also change accordingly.

[0045] In addition, if there are descriptions such as "first" and "second" in the embodiments of the present invention, the descriptions of "first" and "second" are only for descriptive purposes and cannot be understood as indicating or implying their relative importance or implicitly indicating the quantity of the indicated technical features. Thus, the features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In addition, if "and / or" or "and / or" appears throughout the text, its meaning includes three parallel solutions. Taking "A and / or B" as an example, it includes solution A, solution B, or a solution where A and B are satisfied simultaneously. In addition, the technical solutions between the embodiments can be combined with each other, but it must be based on the ability of those of ordinary skill in the art to implement. When the combination of technical solutions results in contradictions or cannot be implemented, it should be considered that such a combination of technical solutions does not exist and is not within the protection scope required by the present invention.

[0046] With the continuous progress of heat pump technology, people are paying increasing attention to the heating capacity and energy efficiency performance of compressors in low-temperature environments. For traditional compressors in low-temperature conditions, their heating capacity often significantly decreases. The main reason is the increase in compression ratio, 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. To solve the problems of heating capacity and energy efficiency at low temperatures, the jet injection enthalpy technology is introduced to effectively increase the suction volume of the compressor. At the same time, the multi-stage compression method can avoid too high a compression ratio for each stage of the compression cylinder, thereby improving the volumetric efficiency. However, how to reduce the superheat problem of the second-stage suction while increasing the supplementary gas volume remains an urgent challenge to be solved.

[0047] The present invention proposes a compressor 100, aiming to solve the problem of how to reduce the superheat of the second-stage suction while increasing the supplementary gas volume in a jet injection enthalpy compressor.

[0048] Please refer to Figures 1 to 3 , in an embodiment of the present invention, the compressor 100 includes a housing 1, a first liquid storage tank 2, a second liquid storage tank 3, a first cylinder 4, and a second cylinder 5. The housing 1 has an installation cavity. An air suction port a and a supplementary gas port b communicating with the installation cavity are opened on the housing 1. The air suction port a and the supplementary gas port b are oppositely arranged in the axial direction of the housing 1. The first liquid storage tank 2 is communicated with the supplementary gas port b. The second liquid storage tank 3 is communicated with the air suction port a. The second liquid storage tank 3 and the first liquid storage tank 2 are staggeredly arranged in the circumferential direction of the housing 1. The first cylinder 4 is arranged in the housing 1. The first cylinder 4 includes a first cylinder block 41. The first cylinder block 41 has a first working cavity c, a first intake hole d and a first exhaust hole e communicating with the first working cavity c. The first intake hole d is communicated with the air suction port a. The second cylinder 5 is arranged in the housing 1. The second cylinder 5 includes a second cylinder block 51. The second cylinder block 51 has a second working cavity f, a second intake hole g and a second exhaust hole communicating with the second working cavity f. The second intake hole g is communicated with the first exhaust hole e. The second exhaust hole is communicated with the installation cavity. A jet hole k is further arranged on the second cylinder block 51. The jet hole k communicates the second intake hole g and the supplementary gas 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 intake hole g is R, the diameter of the jet 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 housing 1 is θ, and 0.2 ≤ V2 / V1 * (R / D) / θ ≤ 1.82.

[0049] It is understandable that the housing 1 is the outer shell of the compressor 100, and an installation cavity is provided inside it. The suction port a and the gas supplement port b are holes opened on the housing 1, which are communicated with the installation cavity and are used for suction and gas supplement respectively. They are arranged oppositely in the axial direction of the housing 1 to facilitate the inlet and outlet of gas.

[0050] The first liquid storage tank 2 is connected to the gas supplement port b and is used for supplementing gas. The second liquid storage tank 3 is connected to the suction port a and is used for storing the inhaled gas.

[0051] The compression assembly includes at least two compression assemblies to form a two-stage compressor 100. The first cylinder 4 is located inside the housing 1 and includes a first cylinder block 41, which has a first working cavity c, an intake hole, and an exhaust hole. The first intake hole d is directly connected to the suction port a and is responsible for inhaling gas. The second cylinder 5 is also located inside the housing 1 and includes a second cylinder block 51, which has a second working cavity f, an intake hole, and an exhaust hole. The second intake hole g is connected to the first exhaust hole e. In this way, the gas after the first-stage compression will enter the second-stage compression. The injection hole k is located on the second cylinder block 51 and connects the second intake hole g and the gas supplement port b, and is used for cooling the gas during the second-stage compression process, reducing gas expansion loss, improving energy efficiency, and enhancing the second-stage compression efficiency.

[0052] 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 characterizes the matching degree between the two compression stages. A reasonable displacement ratio can ensure that the discharged 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.

[0053] If the displacement of the second cylinder 5 is too large and the displacement of the first cylinder 4 is too small, it will cause insufficient gas inhaled by the second cylinder 5, thereby affecting its working efficiency and compression performance.

[0054] If the displacement of the second cylinder 5 is too small, it may cause the gas to stay inside the compression cylinder, forming local overheating; on the contrary, it may cause poor gas flow, affecting the normal operation of the compressor 100. Therefore, it is necessary to comprehensively consider the displacement ratio of the first and second cylinders 5.

[0055] If the displacement of the second cylinder 5 is appropriate, it can ensure that sufficient refrigerant and gas enter, so as to absorb part of the heat during the compression process and slow 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 inside the second cylinder 5 and reducing the overheating phenomenon.

[0056] 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.

[0057] 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.

[0058] 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.

[0059] 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.

[0060] 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.

[0061] 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.

[0062] Specifically, in this embodiment, 0.3≤R / D≤1.67.

[0063] 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.

[0064] When R / D is less than 0.3, it indicates that the radius of the second intake hole g is too small relative to the diameter of the injection hole k. Then, the intake air volume of the second cylinder 5 is relatively small, and the air supplement volume of the injection hole k is relatively large. If the intake air volume is insufficient and the air supplement volume is too large, the refrigeration capacity of the refrigeration system is greater than the load demand, resulting in uneven refrigeration effect, with some areas being supercooled while the temperature in other areas cannot reach the set value. The refrigeration capacity of the entire system still cannot meet the design requirements, leading to the product temperature not meeting the demand.

[0065] Insufficient intake air volume causes the compressor 100 to operate under non-optimal conditions, thereby reducing the overall energy efficiency ratio (COP). Even if a large amount of low-temperature refrigerant is replenished, if the gas is not fully compressed and utilized, the overall efficiency will still be affected.

[0066] In this way, 0.3 ≤ R / D ≤ 1.67 is ensured to make the compressor 100 operate in the best working state, improve the compression efficiency, thereby increasing the energy efficiency ratio (EER or COP) of the system. At the same time, it reduces the retention and resistance of the refrigerant in the pipeline, improves the overall heat exchange efficiency, effectively controls the intake air temperature of the compressor 100, prevents overheating or overcooling, and thus improves the stability and reliability of the system.

[0067] Furthermore, please refer to Figure 2 , in this embodiment, θ ≤ 90°.

[0068] In this way, when 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 housing 1 is set to be less than or equal to 90°, by reasonably setting the connection length between the second liquid storage tank 3 or the first liquid storage tank 2 and the housing 1 through the connecting pipe, as well as the bending angle, the air supplement volume of the refrigerant gas can reach a more reasonable level.

[0069] Specifically, please refer to Figure 3 , in this embodiment, the compressor 100 further includes a partition 6 disposed between the first cylinder block 41 and the second cylinder block 51. A buffer groove m is provided on the end face of the partition 6 facing the first cylinder block 41. A communication hole n communicating with the buffer groove m and penetrating through the other end face is also provided on the partition 6. The buffer groove m communicates with the first exhaust hole e, and the communication hole n communicates with the second intake hole g.

[0070] It can be understood that the buffer groove m is provided on one side of the partition 6 (the end face facing the first cylinder block 41). The buffer groove m is convenient for adjusting the pressure or flow rate.

[0071] The buffer groove m is communicated with the first exhaust hole e, and the gas discharged from the first cylinder block 41 can flow into the buffer groove m. The communication hole n is communicated with the second intake hole g, and the gas in the buffer groove m flows to the second cylinder block 51 through the communication hole n.

[0072] The effective regulation and control of the gas are realized through the partition plate 6, the buffer groove m and the communication hole n, which helps to improve the efficiency of the compressor 100 and avoid the pressure fluctuation caused by the instantaneous gas flow. The existence of the buffer groove m can absorb some vibrations or impacts generated during the gas flow process, thereby protecting other components of the compressor 100. Through reasonable air flow design, the gas flow balance between the first cylinder block 41 and the second cylinder block 51 is ensured, and the overall performance is improved.

[0073] Further, please continue to refer to Figure 3 , in this embodiment, in the direction away from the partition plate 6, the second intake hole g is inclined towards the middle of the second cylinder block 51.

[0074] By arranging the second intake hole g in an inclined manner, the second intake hole g can better guide the gas to flow in, reduce the air flow resistance, enhance the fluidity and inlet efficiency of the gas. The gas is evenly distributed to the middle of the second cylinder block 51, improving the filling efficiency of the cylinder and ensuring the full utilization of the gas in each working cycle. The inclined intake hole can reduce the eddy current 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.

[0075] Further, please refer to Figure 4 , in this embodiment, the cross-sectional area of the second intake hole g is S1, and the cross-sectional area of the communication hole n is S2, and 0.2 ≤ S2 / S1 ≤ 1.2.

[0076] The cross-sectional area (S1) of the second intake hole g: refers to the area size of the second intake hole g in the direction perpendicular to the air flow direction, characterizing the size of the air flow channel.

[0077] The cross-sectional area (S2) of the communication hole n: refers to the cross-sectional area of the communication hole n, indicating the ability of the gas to pass through the communication hole n.

[0078] The ratio of the cross-sectional area S2 of the communication hole n to the cross-sectional area S1 of the second intake 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.

[0079] If S2 is too small (for example, S2 / S1 < 0.2), the resistance of the air flow entering the communication hole n increases, which in turn affects the filling efficiency of the second cylinder block 51.

[0080] If S2 is too large (for example, S2 / S1 > 1.2), it will cause uneven gas flow, resulting in pressure fluctuations and reduced efficiency.

[0081] An appropriate area ratio helps ensure that there are not too many vortices or losses when the gas passes through the communication hole n, thereby improving the efficiency of the entire compressor 100.

[0082] Specifically, please refer to Figure 3 and Figure 4 In this embodiment, the first cylinder block 41 further has a first sliding groove that is communicatively connected to the first working chamber c and extends along the radial direction of the first cylinder block 41. The first cylinder 4 further includes a first sliding vane and a first rolling piston 42. The first sliding vane is radially and telescopically installed in the first sliding groove along the first cylinder block 41. The first rolling piston 42 is driven by the crankshaft to swing eccentrically in the first compression chamber, so as to drive the first sliding vane to move during its swinging stroke. The second cylinder block 51 further has a second sliding groove 51a that is communicatively connected to the second working chamber f and extends along the radial direction of the second cylinder block 51. The second cylinder 5 further includes a second sliding vane 52 and a second rolling piston 53. The second sliding vane 52 is radially and telescopically installed in the second sliding groove 51a along the second cylinder block 51. The second rolling piston 53 is driven by the crankshaft to swing eccentrically in the second compression chamber, so as to drive the second sliding vane 52 to move during its swinging stroke. Wherein, the first sliding vane and the second sliding vane 52 are oppositely arranged in the axial direction of the housing 1.

[0083] It should be noted that, in order to optimize the working efficiency and performance of the compressor 100, ensure that when one compression cylinder in the two compression assemblies exhausts, the other compression cylinder can intake air, and the coordinated cooperation can achieve smoother air flow and pressure changes and reduce pulsation. The sliding vanes of the first cylinder 4 and the second cylinder 5 can be arranged to be oppositely arranged in the axial direction of the housing 1. When the crankshaft rotates, the two eccentric parts respectively drive the corresponding rolling pistons to drive the sliding vanes to move in the radial direction of the cylinder in opposite directions, realizing synchronous intake and exhaust, and effectively reducing the pressure fluctuations caused by the asynchronous operation between the compression cylinders.

[0084] Correspondingly, because the first sliding vane and the second sliding vane 52 are oppositely arranged in the axial direction of the housing 1, and once the position of the sliding vane is determined, the position of the intake port of the corresponding cylinder can be basically determined, that is, the extending direction of the first intake hole d of the first cylinder block 41 and the extending direction of the injection hole k of the second cylinder block 51 are also oppositely arranged in the axial direction of the housing 1. So that when the first cylinder 4 and the second cylinder 5 intake air, the air flow can smoothly flow into the corresponding cylinders along the radial direction of the housing 1.

[0085] Further, in some other embodiments, a connecting groove is recessed in the outer peripheral wall of the second rolling piston 53; the second sliding vane 52 has a connecting post that is close to the second rolling piston 53 and is engaged with the connecting groove, so that the second rolling piston 53 can swing around the connecting post of the second sliding vane 52.

[0086] When the second rolling piston 53 eccentrically swings in the second working chamber f, the engagement between the connecting post of the second sliding vane 52 and the connecting groove ensures that the second rolling piston 53 can swing around the connecting post of the second sliding vane 52, and at the same time, the second sliding vane 52 can move freely in the radial direction, thereby forming a variable compression chamber to realize the suction, compression, and discharge of gas. The connecting groove and the connecting post of the second sliding vane 52 are always in surface contact, reducing the possibility of air leakage from the exhaust side to the suction side, and greatly improving the operating efficiency of the compressor 100.

[0087] The present invention also provides a refrigeration device, which can 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 embodiments. Since this refrigeration device adopts all the technical solutions of the above embodiments, it at least has all the beneficial effects brought by the technical solutions of the above embodiments, which will not be elaborated here one by one.

[0088] 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 adopts the above-mentioned two-stage compressor 100 to increase the gas supplement amount while reducing the superheat of the second-stage suction.

[0089] The above description is only an exemplary embodiment of the present invention, and does not limit the patent scope of the present invention. Any equivalent structural transformation made under the technical concept of the present invention by using the content of the specification and drawings of the present invention, or directly / indirectly applied to other related technical fields, is 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 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.

4. The compressor according to claim 3, 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.

5. The compressor according to claim 3 or 4, 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.

6. 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.

7. The compressor according to claim 6, 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.

8. A refrigeration device, characterized in that: Comprising a compressor as claimed in any one of claims 1 to 7.

9. The refrigeration device according to claim 8, characterized in that: The refrigeration equipment comprises a heat pump.

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