Compressors and refrigeration equipment

Abstract

The present invention discloses a compressor and a refrigeration device, and relates to the technical field of compressors, wherein the compressor comprises a casing, and a first cylinder arranged in the casing, the first cylinder comprises a first cylinder body, a first rolling piston and a first sliding plate, the outer peripheral wall of the first rolling piston is concavely provided with a connecting groove; the first sliding plate is arranged in the first sliding groove, the radius of the connecting column of the first sliding plate and the connecting groove is R, the displacement of the first cylinder body is V, 0.023≤V / R 2 ≤0.61, ensuring that the connecting column of the first sliding plate can withstand a sufficiently large gas force, ensuring the reliability of the cooperation between the first sliding plate and the first rolling piston, while avoiding the increase in power consumption caused by an excessively large contact area between the connecting column of the first sliding plate and the first rolling piston, and also avoiding weakening the strength of the first rolling piston.

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] In a two-stage compressor, by distributing the total pressure ratio to two compression stages, the equipment can maintain a high volumetric efficiency under high pressure ratio operating conditions, and is suitable for low-temperature heating and high-temperature refrigeration scenarios that require enthalpy increase technology. However, this design also brings challenges. Specifically, in the two-stage compression cylinder, due to the high back pressure, the front end of the vane is affected by both medium and high pressure. When the compressor is under light load, the front end of the vane may separate from the rotating roller, causing repeated collisions between the vane and the roller, generating low-frequency noise.

[0003] To solve this problem, the vane structure can be optimized to prevent it from detaching from the roller. Consider using an articulated connection to establish a stable connection between the vane and the roller. This not only helps prevent the vane from detaching, but also ensures that an effective oil film is formed between the front end of the vane and the roller, thereby improving the lubrication effect and further improving the overall performance of the compressor. However, ensuring that the articulated connection between the vane and the roller is both stable and reliable is still a technical problem that needs to be solved. Summary of the invention

[0004] The main purpose of the present invention is to provide a compressor and a refrigeration device, aiming to provide a compressor that ensures that the hinged connection between the sliding vane and the roller is both stable and reliable.

[0005] To achieve the above object, the compressor provided by the present invention comprises a casing and a first cylinder arranged in the casing, wherein the first cylinder comprises:

[0006] a first cylinder body, and a first slide groove on an inner side wall of the first cylinder body;

[0007] A first rolling piston, wherein a connecting groove is formed in an outer peripheral wall of the first rolling piston; and

[0008] A first sliding plate is disposed in the first sliding groove, and a connecting column is disposed at the end of the first sliding plate, and the connecting column is rotatably matched with the connecting groove;

[0009] Wherein, the radius of the connecting column is R, the displacement of the first cylinder is V, 0.023≤V / R 2 ≤0.61.

[0010] In one embodiment, the first slide plate includes a main body section disposed in the first slide groove, and a connecting section connecting the main body section and the connecting column, wherein the connecting section is provided with a chamfer at a notch corresponding to the connecting groove; and / or,

[0011] The connecting groove is provided with a chamfer at the periphery of the groove opening.

[0012] In one embodiment, the first cylinder has a first cavity and a second cavity respectively disposed on both sides of the first sliding plate;

[0013] The compressor also includes a bearing, the bearing cover is arranged on the end surface of the first cylinder body, the bearing is provided with an exhaust port, the exhaust port is connected to the second cavity, and the exhaust port and the first slide groove are at least partially overlapped in the axial direction of the first cylinder body.

[0014] In one embodiment, a cross-sectional area of ​​the exhaust port is S, a projected area of ​​an overlapping region between the exhaust port and the first slide groove in the axial direction of the first cylinder body is S1, and S1≤0.2S.

[0015] In one embodiment, the thickness of the first sliding sheet is t, and 2R≤t.

[0016] In one embodiment, 2R / t≥0.8.

[0017] In one embodiment, the compressor further comprises a second cylinder disposed in the casing, wherein the second cylinder comprises:

[0018] A second cylinder body, wherein the first cylinder is provided with a second air inlet, a second air outlet and a second slide groove provided on the inner wall of the second cylinder body;

[0019] a second rolling piston; and

[0020] The second sliding plate is arranged in the second sliding groove, and one end of the second sliding plate close to the second rolling piston abuts against the second rolling piston, so that the second sliding plate can be driven to move during the moving stroke of the second rolling piston.

[0021] In one embodiment, the ratio of the maximum length of the first sliding plate exposed outside the first sliding groove to the length of the first sliding plate is e1, and the ratio of the maximum length of the second sliding plate exposed outside the second sliding groove to the length of the second sliding plate is e2, wherein e1≤e2.

[0022] In one embodiment, the length of the first sliding piece is L1, the length of the second sliding piece is L2, 1≤L1 / L2≤1.5; and / or,

[0023] The height of the first sliding sheet is h1, the height of the second sliding sheet is h2, and h1≤h2.

[0024] The present invention further provides a refrigeration device, the refrigeration device comprising a compressor, the compressor comprising a casing and a first cylinder arranged in the casing, the first cylinder comprising:

[0025] a first cylinder body, and a first slide groove on an inner side wall of the first cylinder body;

[0026] A first rolling piston, wherein a connecting groove is formed in an outer peripheral wall of the first rolling piston; and

[0027] A first sliding plate is disposed in the first sliding groove, and a connecting column is disposed at the end of the first sliding plate, and the connecting column is rotatably matched with the connecting groove;

[0028] Wherein, the radius of the connecting column is R, the displacement of the first cylinder is V, 0.023≤V / R 2 ≤0.61.

[0029] In one embodiment, the refrigeration device includes an air conditioner.

[0030] In the technical solution of the present invention, a first cylinder is arranged in the housing, the first cylinder includes a first cylinder body, a first rolling piston and a first sliding plate, a connecting groove is recessed on the outer peripheral wall of the first rolling piston, the first sliding plate has a connecting column matched with the connecting groove, so that the first rolling piston can swing around the connecting column of the first sliding plate, and the radius R of the connecting column of the first sliding plate and the displacement V of the first cylinder are set to satisfy the relationship: 0.023≤V / R 2 When ≤0.61, it is ensured that the connecting column of the first sliding plate can withstand a sufficiently large gas force, and the reliability of the cooperation between the first sliding plate and the first rolling piston is ensured, while avoiding the increase in power consumption caused by an excessively large contact area between the connecting column of the first sliding plate and the first rolling piston, and also avoiding weakening the strength of the first rolling piston, so as to provide a compressor that ensures that the hinged connection between the sliding plate and the roller is both stable and reliable. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] 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.

[0032] Figure 1 A cross-sectional schematic diagram of an embodiment of a compressor provided by the present invention;

[0033] Figure 2 for Figure 1Schematic diagram of the cross section at AA in the middle;

[0034] Figure 3 for Figure 2 A partial enlarged view of point B in the middle;

[0035] Figure 4 is a schematic diagram of the positional relationship of the exhaust port of the bearing projected onto the first cylinder;

[0036] Figure 5 A curve diagram of the stress life cycle number of the compressor provided by the present invention;

[0037] Figure 6 A graph showing the COP performance level of the compressor provided by the present invention.

[0038] Description of Figure Numbers:

[0039] 100. Compressor; 1. Casing; 2. First cylinder; 21. First cylinder body; a. First working chamber; a1. First chamber body; a2. Second chamber body; b. First slide groove; 22. First rolling piston; c. Connecting groove; 23. First slide vane; 231. Connecting column; d. Exhaust port; 3. Second cylinder; 31. Second cylinder body; 32. Second rolling piston; 33. Second slide vane; 4. Bearing.

[0040] 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

[0041] 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.

[0042] 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.

[0043] 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.

[0044] In a two-stage compressor, by allocating the total pressure ratio to two compression stages, the equipment can maintain a high volumetric efficiency under high pressure ratio operating conditions, and is suitable for low-temperature heating and high-temperature cooling scenarios that require enthalpy increase technology. However, this design also brings challenges. Specifically, in the two-stage compression cylinder, due to the high back pressure, the front end of the vane is affected by both medium and high pressure. When the compressor is under light load, the front end of the vane may separate from the rotating roller, causing repeated collisions between the vane and the roller, generating low-frequency noise. To solve this problem, the vane structure can be optimized to prevent it from detaching from the roller. Consider using an articulated connection to establish a stable connection between the vane and the roller. This not only helps to prevent the vane from detaching, but also ensures that an effective oil film is formed between the front end of the vane and the roller, thereby improving the lubrication effect and further improving the overall performance of the compressor. However, ensuring that the articulated connection between the vane and the roller is both stable and reliable is still a technical problem that needs to be solved.

[0045] The present invention provides a compressor, aiming to provide a compressor which ensures that the hinged connection between the sliding vane and the roller is both stable and reliable.

[0046] See also Figure 1 and Figure 2In one embodiment of the present invention, the compressor 100 includes a casing 1 and a first cylinder 2 arranged in the casing 1, the casing 1 is provided with an air intake port and an air outlet, the first cylinder 2 includes a first cylinder body 21, a first rolling piston 22 and a first sliding vane 23, the first cylinder body 21 has a first working chamber a, and a first slide groove b connected to the first working chamber a, the first slide groove b extends along the radial direction of the first cylinder body 21; the first rolling piston 22 is used to be driven by the crankshaft to eccentrically swing in the first working chamber a, and the outer peripheral wall of the first rolling piston 22 is recessed with a connecting groove c; the The first slide plate 23 is slidably installed in the first slide groove b along the radial direction of the first cylinder body 21. The first slide plate 23 has a thickness direction extending along the circumferential direction of the first rolling piston 22. The first slide plate 23 has a connecting column 231 close to the first rolling piston 22 and matched with the connecting groove c. The end surface of the connecting column 231 is spherical so that the first rolling piston 22 can swing around the connecting column 231 of the first slide plate 23; wherein the radius of the connecting column 231 of the first slide plate 23 is R, the displacement of the first cylinder 2 is V, 0.023≤V / R 2 ≤0.61.

[0047] It should be noted that the first cylinder body 21 is the main body of the first cylinder 2, has a certain shape and size, and is generally set to a cylindrical shape. The first working chamber a is a space inside the first cylinder body 21, which is used to accommodate the first rolling piston 22 and the first sliding plate 23 and perform a compression process. The first sliding groove b is a groove arranged along the radial direction of the first cylinder body 21, which is used to install the first sliding plate 23 so that the first sliding plate 23 can move freely in the radial direction.

[0048] The first rolling piston 22 is a component eccentrically installed in the first cylinder body 21, and its shape is set to be cylindrical, but the central axis does not coincide with the central axis of the first cylinder body 21. The connecting groove c is a groove arranged on the outer peripheral wall of the first rolling piston 22, and is used to accommodate the connecting column 231 of the first sliding plate 23.

[0049] The first sliding vane 23 is a component that can move radially along the first cylinder body 21 and is used to contact with the wall of the first cylinder body 21 to form a compression chamber.

[0050] The thickness direction of the first sliding sheet 23 refers to the direction of the first sliding sheet 23 along the circumference of the first rolling piston 22. The connecting column 231 of the first sliding sheet 23 is a part of the first sliding sheet 23, and is used to cooperate with the connecting groove c of the first rolling piston 22.

[0051] It should also be noted that the connecting column 231 of the first sliding plate 23 is designed with an arc surface, and the contact area between it and the first rolling piston 22 is a surface contact. When the rolling piston swings around the sliding plate, the gas force acting on the sliding plate is related to the size of the arc surface, and the stress in the arc surface contact is usually distributed according to the inverse square law of the distance.

[0052] Specifically, R 2 Characterizes the strength of the connecting column 231 of the first sliding sheet 23 . The larger the cross-sectional area of ​​the connecting column 231 , the greater the connecting strength of the first sliding sheet 23 .

[0053] When V is constant and the gas load is constant, R 2 The smaller the V / R is, the easier it is for the connecting column 231 of the first sliding vane 23 to undergo plastic deformation, which will affect the smoothness of the swing between the connecting column 231 of the first sliding vane 23 and the connecting groove c of the first rolling piston 22 to a certain extent, causing the compressor to jam during operation, increase input power, and lead to performance degradation. 2 >0.61, under extreme working conditions, the connection between the connecting column 231 of the first sliding plate 23 and the connecting groove c of the first rolling piston 22 breaks and fails.

[0054] On the contrary, R 2 The larger the thickness of the first vane 23 is, the stronger the connection strength of the first vane 23 is, and the deformation during operation can be effectively avoided. However, the thickness of the first vane 23 will also increase, so the cross-sectional area of ​​the connecting column 231 of the first vane 23 increases, and the contact force between the first vane 23 and the first rolling piston 22 is provided by the back pressure of the first vane 23. The contact force F is equal to the back pressure P of the first vane 23 multiplied by the cross-sectional area S of the first vane 23 (that is, the thickness of the first vane 23 multiplied by the height of the first vane 23). When the thickness of the first vane 23 increases, the contact force F also increases, resulting in the deterioration of the friction between the first vane 23 and the first rolling piston 22, which will eventually lead to a decrease in the performance of the compressor.

[0055] In the technical solution of the present invention, a first cylinder 2 is arranged in the housing 1, and the first cylinder 2 includes a first cylinder body 21, a first rolling piston 22 and a first sliding plate 23. A connecting groove c is recessed on the outer peripheral wall of the first rolling piston 22, and the first sliding plate 23 has a connecting column 231 that matches the connecting groove c, so that the first rolling piston 22 can swing around the connecting column 231 of the first sliding plate 23, and the radius R of the connecting column 231 and the displacement V of the first cylinder 2 are set to satisfy the relationship: 0.023≤V / R 2When ≤0.61, it is ensured that the connecting column 231 of the first slide 23 can withstand a sufficiently large gas force, and the reliability of the cooperation between the first slide 23 and the first rolling piston 22 is ensured, while avoiding the increase in power consumption caused by an excessively large contact area between the connecting column 231 of the first slide 23 and the first rolling piston 22, and also avoiding weakening the strength of the first rolling piston 22, so as to provide a compressor 100 that ensures that the hinged connection between the slide and the roller is both stable and reliable.

[0056] See also Figure 5 and Figure 6 , Figure 5 The graph shown is a graph of the stress life cycle number of the compressor provided by the present invention. Figure 6 A graph showing the COP performance level of the compressor provided by the present invention.

[0057] exist Figure 5 In the figure, the horizontal axis corresponds to the number of times the compressor can operate normally (life cycle number), and the vertical axis represents the stress value of the compressor application scenario.

[0058] The compressor has declared performance parameters and operating range (optimal and worst conditions). The maximum stress value F0 corresponding to the compressor under the worst condition is Figure 5 The maximum stress line ①.

[0059] The four curves ②③④⑤ correspond to the sliders made of four different materials in this application (from top to bottom, the material strength decreases in turn), and when V / R 2 Satisfy 0.023≤V / R 2 When ≤0.61, the relationship between the stress on the compressor and the number of normal operations. When the stress is greater and the vane size is constant, the number of operations that can be performed shows a downward trend.

[0060] The compressor life cycle is set to 10 4 For example, the four curves ②③④⑤ correspond to the maximum stress F that the sliding vanes made of four different materials in this application can withstand, and are all greater than the corresponding maximum stress value F0 declared by the compressor.

[0061] In other words, taking curve ⑤ as an example, when the actual number of cycles of the compressor reaches the declared service life cycle number of 10 4 When the sliding plate used in this application is subjected to a stress F greater than F0 (i.e., the horizontal coordinate of curve ⑤ corresponds to 10 4 When the value corresponding to the ordinate is greater than F0), the slide can continue to work and the number of cycles reaches 10. 4 to 10 5When the sliding plate is between the points where the curve ⑤ intersects the straight line ①, the maximum stress F that the sliding plate can actually withstand at the moment reaches F0. When the sliding plate continues to work, the sliding plate will deform or even break, indicating that the actual number of life cycles of the technical solution of the present application is greater than the declared number of life cycles.

[0062] Therefore, according to Figure 5 The curve shown can clearly show that when V / R 2 Satisfy 0.023≤V / R 2 ≤0.61, which can satisfy the declared operating range of the compressor.

[0063] Figure 6 In the figure, the horizontal axis corresponds to V / R 2 The vertical axis corresponds to the COP coefficient of performance of the compressor, which is the ratio of the heat provided by the compressor (in the case of heating) or the heat removed (in the case of cooling) per unit time to the workload (usually electrical energy) consumed in the same period of time. The higher the COP value, the more efficient the compressor.

[0064] Therefore, according to Figure 6 The curve shown can clearly show that when V / R 2 Satisfy 0.023≤V / R 2 When ≤0.61, the COP performance coefficient of the compressor is in a better state.

[0065] Further, in order to avoid interference between the first slide plate 23 and the first rolling piston 22 at the limit position, resulting in a stuck phenomenon during operation, please refer to Figure 2 and Figure 3 In the present embodiment, the first slide plate 23 includes a main body section arranged in the first slide groove b, and a connecting section connecting the main body section and the connecting column 231, and the connecting section is provided with a chamfer at the notch corresponding to the connecting groove c; and / or, a chamfer is provided at the peripheral edge of the notch of the connecting groove c.

[0066] Thus, when the first rolling piston 22 rotates relative to the first sliding plate 23, the chamfer can reduce the stress concentration at the notch, preventing the first sliding plate 23 or the first rolling piston 22 from cracking or being damaged there. In addition, the chamfer provides a smooth transition, which helps the end of the first sliding plate 23 to cooperate with the connecting groove c more smoothly, reduces the sticking phenomenon, and the wear between the first sliding plate 23 and the notch of the connecting groove c, prolongs the service life of the first sliding plate 23 and the first rolling piston 22, and can form a more stable oil film between the two, thereby improving the lubrication condition.

[0067] The chamfer is preferably an arc chamfer. Of course, it can also be other possible shapes, which are not limited in this specification.

[0068] It should be noted that when the compression cylinder is compressing, all the gas in the working chamber needs to be discharged to avoid the refrigerant gas remaining in the compression cylinder during the next suction process. The refrigerant gas expands and occupies part of the space that should be filled with fresh gas, thereby affecting the volumetric efficiency of the compressor 100.

[0069] However, due to the existence of the chamfers of the first sliding plate 23 and the connecting groove c of the first rolling piston 22, an additional small space (i.e., clearance volume) may be formed on the exhaust side of the first cylinder 2. The gas in this space cannot be completely discharged, and will expand at the beginning of the next compression cycle, occupying a part of the effective working volume, resulting in a decrease in volumetric efficiency. The clearance volume on the exhaust side will increase, and the volumetric efficiency of the compression cylinder will decrease.

[0070] For further information, see Figures 1 to 4 In this embodiment, the first cylinder 2 has a first cavity a1 and a second cavity a2 respectively arranged on both sides of the first sliding vane 23; the compressor 100 also includes a bearing 4, the bearing 4 is covered on the end surface of the first cylinder 21, and an exhaust port d is arranged on the bearing 4, the exhaust port d is connected to the second cavity a2, and the exhaust port d and the first sliding groove b are at least partially overlapped in the axial direction of the first cylinder 21.

[0071] It can be understood that the first sliding vane 23 slides radially in the first working chamber a, dividing it into two parts, the first chamber a1 and the second chamber a2, so that the three stages of suction, compression and discharge are achieved in one working cycle. When compression is completed, the high-pressure gas can be discharged through the exhaust port d.

[0072] It should also be noted that a valve plate is provided on the bearing 4 corresponding to the exhaust port d. When the first cylinder 2 is in the intake and compression stage, the valve plate closes the exhaust port d. When the first cylinder 2 is in the exhaust stage, the valve plate opens until the minimum gap between the first rolling piston 22 and the inner wall of the first cylinder body 21 passes through the exhaust port d, and then the valve plate closes to prepare for intake again.

[0073] In this way, the exhaust port d at least partially overlaps with the first vane 23 in the axial direction, so that the clearance volume at the hinged chamfer can be directly connected to the exhaust port d. In this way, even when the first vane 23 reaches the extreme position, the residual gas can be discharged together with the main working gas instead of being compressed again. The high-pressure gas in the second cavity a2 can be quickly and effectively discharged through the exhaust port d, which not only reduces the over-compression phenomenon caused by the clearance volume and does not cause excessive pressure accumulation, but also improves the overall volumetric efficiency of the compressor 100.

[0074] Furthermore, since the first sliding vane 23 blocks a portion of the exhaust port d, the exhaust area of ​​the exhaust port d is reduced. In order to avoid the increase in flow loss due to the reduction in the exhaust area, in the present embodiment, the cross-sectional area of ​​the exhaust port d is S, and the projection area of ​​the overlapping area between the exhaust port d and the first sliding vane 23 in the axial direction of the first cylinder body 21 is S1, and S1≤0.2S.

[0075] The cross-sectional area S of the exhaust port d refers to the maximum cross-sectional area of ​​the exhaust port d when it is in a fully open state and is not blocked by any components.

[0076] The overlapping region projection area S1 refers to the axial projection area of ​​the overlapping region formed by the first sliding vane 23 shielding the exhaust port d.

[0077] In this way, the ratio is limited to S1≤0.2S, ensuring that the area blocked by the first sliding vane 23 does not exceed 20% of the total area of ​​the exhaust port d, thereby ensuring that even when the sliding vane blocks the exhaust port, there is still a large enough exhaust area to maintain a low flow resistance and avoid a significant increase in flow loss.

[0078] It should be noted that the first sliding vane 23 contacts the wall surface of the sliding groove of the cylinder wall and plays a sealing role during the compression process. The smaller the friction between the first sliding vane 23 and the cylinder wall, the less energy loss and the higher the efficiency of the compressor 100 during operation. In order to ensure that the first sliding vane 23 can effectively seal and reduce wear, it is usually necessary to perform surface treatment on the two side portions in the thickness direction of the first sliding vane 23 to make its surface smoother.

[0079] In order to avoid simultaneous wear of the connecting column 231 of the first sliding sheet 23 when grinding and polishing the two side portions in the thickness direction of the first sliding sheet 23, so that the connecting column 231 of the first sliding sheet 23 cannot fit into the connecting groove c to form surface contact, in this embodiment, the thickness of the first sliding sheet 23 is t, 2R≤t.

[0080] In this way, the thickness t of the first slide 23 is set to be larger than the diameter 2R of the connecting column 231 of the first slide 23. In this way, when the main body of the first slide 23 is polished, the polished surface will not contact the outer surface of the connecting column 231 of the first slide 23, thereby avoiding the wear of the connecting column 231 of the first slide 23. When the size of the connecting column 231 of the first slide 23 exceeds the thickness of the first slide 23, higher requirements will be placed on the processing of the first slide 23, which is not conducive to production and manufacturing.

[0081] Further, in this embodiment, 2R / t≥0.8.

[0082] The diameter (2R) of the connecting column 231 of the first sliding plate 23 determines the contact length with the connecting groove c of the first rolling piston 22. If the diameter of the connecting column 231 of the first sliding plate 23 is too small, the contact length with the first rolling piston 22 will be reduced.

[0083] A shorter contact length indicates that the contact area between the two is reduced, which increases local stress concentration and friction, resulting in increased surface wear of the first sliding vane 23 or the first rolling piston 22, and may even cause mechanical failure. In addition, a smaller diameter may also weaken the structural strength of the first sliding vane 23, making it more likely to deform or break under high load conditions, thereby affecting the long-term operating stability of the compressor 100.

[0084] Further, in the present embodiment, a first air inlet and a first air outlet are also provided on the first cylinder body 21, both of which are connected to the first working chamber a; the compressor 100 also includes a second cylinder 3, the second cylinder 3 includes a second cylinder body 31, a second rolling piston 32 and a second sliding vane 33, the second cylinder body 31 has a second working chamber, and a second air inlet, a second air outlet and a second slide groove connected to the second working chamber, the second air inlet is connected to the air intake port, the second air outlet is connected to the first air inlet, the first air outlet is connected to the refrigerant outlet, and the second slide groove extends along the radial direction of the second cylinder body 31; the second rolling piston 32 is used to be driven by the crankshaft to swing eccentrically in the second working chamber; the second slide vane 33 is telescopically installed in the second slide groove along the radial direction of the second cylinder body 31, and the end of the second slide vane 33 close to the second rolling piston 32 abuts against the second rolling piston 32, so that the second slide vane 33 can be driven to move during the activity stroke of the second rolling piston 32.

[0085] It is understood that the compressor 100 includes two cylinders, so two-stage compression can be achieved, and the refrigerant is first sucked into the low-pressure compression chamber of the first stage for preliminary compression. At this time, the pressure and temperature of the refrigerant will increase. After the first stage compression, the refrigerant will enter an intermediate cooling stage. In this process, a part of the high-temperature and high-pressure gas is discharged from the compressor 100 and reintroduced into the compressor 100 (this process is called injection enthalpy or injection enthalpy increase) to reduce the temperature of the gas entering the second stage compression, thereby reducing power consumption and improving efficiency. The refrigerant after the intermediate cooling treatment is then sent to the second stage compression chamber, where the refrigerant is further compressed to a higher pressure and temperature. Then, the high-pressure and high-temperature refrigerant leaves the compressor 100 and enters the condenser to complete the subsequent refrigeration cycle. Due to the use of injection enthalpy technology, the two-stage compressor 100 can use energy more efficiently, especially when operating at low ambient temperatures, it can provide better heating effects, and can achieve a lower evaporation temperature than the single-stage compressor 100 without causing the compressor 100 to overload.

[0086] Correspondingly, in this embodiment, the second cylinder 3 is set to the first stage compression, and the first cylinder 2 is set to the second stage compression.

[0087] It should also be noted that, since the second slide plate 33 is telescopically installed in the second slide groove along the radial direction of the second cylinder body 31, the end of the second slide plate 33 close to the second rolling piston 32 abuts against the second rolling piston 32, that is, the second slide plate 33 and the second rolling piston 32 are not hinged.

[0088] Furthermore, in this embodiment, the ratio of the maximum length l1 of the first sliding plate 23 exposed outside the first sliding groove b to the length L1 of the first sliding plate 23 is e1, and the ratio of the maximum length l2 of the second sliding plate 33 exposed outside the second sliding groove to the length L2 of the second sliding plate 33 is e2, wherein e1≤e2.

[0089] It should be noted that the ratio of the maximum length l1 of the first slide 23 exposed outside the first slide groove b to the length L1 of the first slide 23 is the extension rate of the first slide 23, and the ratio of the maximum length l2 of the second slide 33 exposed outside the second slide groove to the length L2 of the second slide 33 is the extension rate of the second slide 33.

[0090] A smaller vane extension rate can provide a larger sealing area, which helps to improve compression efficiency and reduce leakage losses. However, if the vane extends too much, it may increase friction loss, and in extreme cases may cause mechanical failure or shorten the life of the vane. Specifically, the vane directly abuts (or contacts) the rolling piston. In order to ensure that the vane can stably abut the rolling piston, the vane extension rate is too large, which can easily cause it to bend or detach during operation. Since the vane needs to slide radially in the cylinder, the larger the cylinder displacement, the greater the eccentricity, resulting in a greater extension rate (that is, the degree to which the vane extends from the slide groove), which will increase mechanical wear and energy loss. In addition, the vane mainly relies on direct contact between the end and the rolling piston to transmit force. Such force distribution may lead to local stress concentration, affecting the service life of the vane and the rolling piston.

[0091] It can be understood that the first slide 23 is hingedly connected to the first rolling piston 22, so that the front end of the first slide 23 has a certain degree of swing freedom, so that the first slide 23 can adaptively adjust its position within a certain range, thereby reducing the extent to which the first slide 23 must extend out of the first slide groove b during operation.

[0092] It should be noted that in order to achieve the best pressure ratio of the cylinder, the height and length of the vane need to be reasonably designed. The pressure ratio refers to the ratio of the exhaust pressure to the suction pressure of the compressor 100. Under certain operating conditions, the best pressure ratio of the compressor 100 refers to the pressure ratio at which the compressor 100 can achieve the highest efficiency and performance.

[0093] The larger the volume of the compression chamber, the higher the height of the vane when the cylinder inner diameter remains unchanged, the greater the vane back pressure, the better the fit between the vane front end and the rolling piston outer diameter, effectively preventing gas leakage from the vane front end under high pressure ratio, thereby improving the volumetric efficiency of the compressor. When the vane height is appropriate, good sealing and compression efficiency can be maintained under different pressure ratios.

[0094] The length of the vane affects the flow path and flow characteristics of the gas in the compression chamber. Longer vanes can provide better gas sealing and flow control, so that the compressor 100 can effectively compress the gas to the required pressure under high pressure ratio.

[0095] Therefore, the height and length of the vane, the rotation speed of the compressor 100, the properties of the gas (such as temperature, density, etc.), and the design parameters of the compressor 100 (such as the shape of the cylinder, the material of the vane, etc.) will jointly affect the optimal pressure ratio of the compressor 100. In order to ensure that the compressor 100 can achieve the best performance under specific working conditions, it is necessary to optimize the size of the vane to ensure that the compressor 100 can operate within the ideal pressure ratio range in specific application scenarios (such as air conditioning, refrigeration, gas transmission, etc.) to maximize its efficiency and reliability.

[0096] e1 is set to be less than or equal to e2. The lower extension rate reduces the mechanical wear and friction loss between the first slide 23 and the first cylinder 21. Due to the reduction in mechanical wear and friction loss, and the optimization of the force condition of the slide, the working efficiency of the entire system is improved. Higher working efficiency is directly converted into lower power consumption, that is, less energy is consumed under the same working conditions, and heat and other forms of energy loss are also reduced.

[0097] Furthermore, in one embodiment, 1≤L1 / L2≤1.5, the height of the first sliding piece 23 is h1, the height of the second sliding piece 33 is h2, and h1≤h2.

[0098] See also Figure 1 The height h1 and h2 of the sliding vane refers to the vertical length of the sliding vane from the bottom to the top thereof in the working state, that is, the dimension in the axial direction of the first cylinder body 21 or the second cylinder body 31 .

[0099] In this way, the ratio between the length L1 of the first slide 23 and the length L2 of the second slide 33 is limited to between 1 and 1.5, and the ratio between the height h1 of the first slide 23 and the height h2 of the second slide 33 is limited to less than or equal to 1, so as to ensure the sealing and flow performance of the slide during operation, prevent gas leakage and improve compression efficiency.

[0100] The present invention further proposes a refrigeration device, which includes an air conditioner, 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 repeated here.

[0101] In a specific embodiment, the air conditioner adopts the above-mentioned compressor 100, so that the air conditioner has good stability and reliability during actual use.

[0102] 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: The invention comprises a casing and a first cylinder disposed in the casing, wherein the first cylinder comprises: A first cylinder body, wherein the inner side wall of the first cylinder body is provided with a first slide groove; A first rolling piston, wherein a connecting groove is formed in an outer peripheral wall of the first rolling piston; and A first sliding plate is disposed in the first sliding groove, and a connecting column is disposed at the end of the first sliding plate, and the connecting column is rotatably matched with the connecting groove; Wherein, the radius of the connecting column is R, the displacement of the first cylinder is V, 0.023≤V / R 2 ≤0.61; The first cylinder has a first cavity and a second cavity respectively arranged on both sides of the first sliding plate; The compressor further comprises a bearing, wherein the bearing cover is arranged on the end surface of the first cylinder body, and an exhaust port is arranged on the bearing, wherein the exhaust port is communicated with the second cavity, and the exhaust port and the first slide groove are at least partially overlapped in the axial direction of the first cylinder body; The cross-sectional area of ​​the exhaust port is S, and the projected area of ​​the overlapping region between the exhaust port and the first slide groove in the axial direction of the first cylinder body is S1, where S1≤0.2S.

2. The compressor according to claim 1, characterized in that The first sliding sheet includes a main body section arranged in the first sliding groove, and a connecting section connecting the main body section and the connecting column, wherein the connecting section is provided with a chamfer at a notch corresponding to the connecting groove; and / or, The connecting groove is provided with a chamfer at the periphery of the groove opening.

3. The compressor according to claim 1, characterized in that The thickness of the first sliding sheet is t, 2R≤t.

4. The compressor according to claim 3, characterized in that 2R / t≥0.

8.

5. The compressor according to any one of claims 1 to 4, characterized in that: The compressor further includes a second cylinder disposed in the housing, the second cylinder including: A second cylinder body, wherein the second cylinder body is provided with a second air inlet, a second air outlet, and a second slide groove provided on an inner wall of the second cylinder body; a second rolling piston; and The second sliding plate is arranged in the second sliding groove, and one end of the second sliding plate close to the second rolling piston abuts against the second rolling piston, so that the second sliding plate can be driven to move during the moving stroke of the second rolling piston.

6. The compressor according to claim 5, characterized in that The ratio of the maximum length of the first sliding plate exposed outside the first sliding slot to the length of the first sliding plate is e1, and the ratio of the maximum length of the second sliding plate exposed outside the second sliding slot to the length of the second sliding plate is e2, wherein e1≤e2.

7. The compressor according to claim 6, characterized in that The length of the first sliding sheet is L1, the length of the second sliding sheet is L2, 1≤L1 / L2≤1.5; and / or, The height of the first sliding sheet is h1, the height of the second sliding sheet is h2, and h1≤h2.

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 includes an air conditioner.

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