A compressor

Abstract

The present application relates to the technical field of rolling rotor compressor, and particularly relates to a compressor, which comprises a first cylinder, the first cylinder has a first cylinder center axis, the first vertical passage has a first vertical passage center axis, the first exhaust oblique cutout has a first exhaust oblique cutout center axis, a plane formed between the first vertical passage center axis and the first cylinder center axis is defined as a first plane, a plane formed between the first slide slot center axis and the first cylinder center axis is defined as a second plane, the first plane and the second plane have an included angle theta j ; a plane formed between the first exhaust oblique cutout center axis and the first cylinder center axis is defined as a third plane, the third plane and the second plane have an included angle theta e ; theta j and theta e satisfy the following relationship: theta e -5 DEG <= theta j <= theta e +15 DEG. The present application can greatly reduce the processing cost, improve the energy efficiency and reduce the noise.

Description

Technical Field

[0001] This invention relates to the field of rolling rotor compressor technology, and in particular to a compressor. Background Technology

[0002] Jet enthalpy enhancement technology is a core technology for improving the low-temperature heating performance of rolling rotor compressors. It increases the flow rate of the circulating working fluid by supplementing the cylinder with gas during the compression process, thereby improving the compressor's heating capacity and energy efficiency.

[0003] Currently, the rolling rotor compressors on the market have a large air gap volume due to the placement of the jet enthalpy enhancement component on the non-exhaust side. This results in severe refrigerant backflow loss during the compression process, leading to a decrease in the compressor's volumetric efficiency and COP (coefficient of performance). Summary of the Invention

[0004] To overcome at least one of the aforementioned defects and problems in the prior art, the present invention provides a compressor.

[0005] According to a specific embodiment of the present invention, a compressor is provided, including a first cylinder, an upper bearing, and a lower bearing. The first cylinder is disposed between the upper bearing and the lower bearing. The first cylinder has a first cylinder central axis. The first cylinder is provided with a first air supply channel, a first exhaust oblique cut, and a first vane groove. The first air supply channel includes a first transverse channel and a first vertical channel. The first vertical channel has a first vertical channel central axis. The first exhaust oblique cut has a first exhaust oblique cut central axis. The first vane groove has a first vane groove central axis. The compressor further includes a first vapor injection enthalpy enhancement assembly. The first vapor injection enthalpy enhancement assembly is disposed on the upper end face of the first cylinder. The first vapor injection enthalpy enhancement assembly includes a first air supply valve seat, a first air supply valve plate, a first limiter, and a first locking screw installed in the first air supply valve seat. When the first air replenishment valve plate is closed on the first air replenishment channel, the first air replenishment channel and the first exhaust oblique cut are in a non-connected state; when the first air replenishment valve plate is not closed on the first air replenishment channel, the first air replenishment channel and the first exhaust oblique cut are in a connected state. The first locking screw passes through the first limiter and the first air supply valve plate, and is threadedly connected to the first air supply valve seat via the first locking screw. The plane formed between the central axis of the first vertical channel and the central axis of the first cylinder is defined as the first plane, and the plane formed between the central axis of the first sliding groove and the central axis of the first cylinder is defined as the second plane. The first plane and the second plane have an included angle θ. j ; The plane formed between the central axis of the first exhaust oblique cut and the central axis of the first cylinder is defined as the third plane, and the third plane has an angle θ with the second plane. e ; The θ j With the θ e Satisfy the following relationship: θ e -5°≤θ j ≤θ e +15°.

[0006] In a preferred embodiment, θ j With the θ e Satisfying θ j =θ e .

[0007] In a preferred embodiment, the first cylinder has a first inner diameter, the upper bearing has a maximum sealing outer diameter, and the first jet enthalpy enhancement component is disposed between the first inner diameter and the maximum sealing outer diameter of the upper bearing. The first inner diameter is Dc, the maximum sealing outer diameter of the upper bearing is Bc, and the first jet enthalpy enhancement component has a first projected length Lj in the horizontal direction. The Dc, Bc, and Lj satisfy 0.7*(Bc-Dc) / 2≤Lj≤1.3*(Bc-Dc) / 2.

[0008] In a preferred embodiment, the head of the first locking screw is higher than the upper end face of the first cylinder, and the upper bearing has a first clearance hole at the position corresponding to the head of the first locking screw. The depth of the first clearance hole is not less than the height of the head of the first locking screw above the upper end face of the first cylinder.

[0009] In a preferred embodiment, the first clearance hole is a countersunk hole or a blind hole, and a gap of 0.1mm-0.3mm is left between the inner wall of the first clearance hole and the head of the first locking screw.

[0010] In a preferred embodiment, the symmetry center plane of the first jet enthalpy enhancement component is defined as a fourth plane, and the fourth plane has an angle α with the first plane, the angle α satisfying 0°≤α≤65°.

[0011] In a preferred embodiment, the included angle α satisfies 20°≤α≤55°.

[0012] In a preferred embodiment, the center plane of symmetry of the first transverse channel is defined as a fifth plane, which has an angle θp with the second plane. j With the θ p Satisfy: θ p =θ j +8° or θ p=θ j -8°.

[0013] In a preferred embodiment, θ p With the θ j Satisfy: θ p =θ j .

[0014] In a preferred embodiment, the first air replenishment valve is a reed valve, and the first limiter limits the first air replenishment valve by a travel of La, wherein the value of La is in the range of 0.5mm≤La≤2.5mm.

[0015] In a preferred embodiment, the compressor further includes an intermediate partition and a second cylinder, wherein the upper bearing, the first cylinder, the intermediate partition, the second cylinder, and the lower bearing are arranged sequentially. The second cylinder has a second cylinder central axis, and the second cylinder is provided with a second air supply channel, a second exhaust oblique cut, and a second sliding vane groove. The second air supply channel includes a second transverse channel and a second vertical channel. The second vertical channel has a second vertical channel central axis. The second exhaust oblique cut has a second exhaust oblique cut central axis. The second sliding vane groove has a second sliding vane groove central axis. It also includes a second jet enthalpy enhancement assembly. The second jet enthalpy enhancement assembly is disposed on the lower end face of the second cylinder. The second jet enthalpy enhancement assembly includes a second air supply valve seat, a second air supply valve plate, a second limiter, and a second locking screw installed in the second air supply valve seat. When the second air supply valve plate is closed on the second air supply channel, the second air supply channel and the second exhaust oblique cut are in a non-connected state; when the second air supply valve plate is not closed on the second air supply channel, the second air supply channel and the second exhaust oblique cut are in a connected state. The second locking screw passes through the second limiter and the second air supply valve plate and is threadedly connected to the second air supply valve seat through the second locking screw. The plane formed between the central axis of the second vertical channel and the central axis of the second cylinder is defined as the sixth plane. The plane formed between the central axis of the second sliding plate groove and the central axis of the second cylinder is defined as the seventh plane. The sixth plane and the seventh plane have an included angle θh. The plane formed between the central axis of the second exhaust oblique cut and the central axis of the second cylinder is defined as the eighth plane, and the eighth plane has an included angle θi with the seventh plane; The relationship between θh and θi is as follows: θi-5°≤θh≤θi+15°.

[0016] In a preferred embodiment, θh and θi satisfy θh=θi.

[0017] In a preferred embodiment, the second cylinder has a second inner diameter, the lower bearing has a maximum sealing outer diameter, and the second jet enthalpy enhancement assembly is disposed between the second inner diameter and the maximum sealing outer diameter of the lower bearing. The second inner diameter is Dm, the maximum sealing outer diameter of the lower bearing is Bn, and the second jet enthalpy enhancement assembly has a second projected length Lk in the horizontal direction. The relationship between Dm, Bn, and Lk satisfies 0.7*(Bn-Dm) / 2≤Lk≤1.3*(Bn-Dm) / 2.

[0018] In a preferred embodiment, the head of the second locking screw is higher than the lower end face of the second cylinder, and the lower bearing has a second clearance hole at the position corresponding to the head of the second locking screw. The depth of the second clearance hole is not less than the height of the head of the second locking screw above the lower end face of the second cylinder.

[0019] In a preferred embodiment, the second clearance hole is a countersunk hole or a blind hole, and a gap of 0.1mm-0.3mm is left between the inner wall of the second clearance hole and the head of the second locking screw.

[0020] In a preferred embodiment, the symmetry center plane of the second jet enthalpy enhancement component is defined as the ninth plane, and the ninth plane and the sixth plane have an included angle β, which satisfies 0°≤β≤65°.

[0021] In a preferred embodiment, the included angle β satisfies 20°≤β≤55°.

[0022] In a preferred embodiment, the symmetry center plane of the second transverse channel is defined as the tenth plane, and the tenth plane and the seventh plane have an angle θq between them. The θq and θh satisfy: θq=θh+8° or θq=θh-8°.

[0023] In a preferred embodiment, θq and θh satisfy: θq = θh.

[0024] In a preferred embodiment, the second air replenishment valve is a reed valve, and the limiting stroke of the second limiter on the second air replenishment valve is Lb, wherein the value range of Lb is: 0.5mm≤Lb≤2.5mm.

[0025] In a preferred embodiment, the theoretical displacement of the compressor is X, and the horizontal width of the connection between the first vertical channel and the first exhaust oblique cut, or the horizontal width of the connection between the second vertical channel and the second exhaust oblique cut, is Y. X and Y satisfy Y = k * The values ​​of k are in the range of 0.52≤k≤0.68, the values ​​of X are in the range of 55≤X≤75, and the values ​​of Y are in the range of 4≤Y≤6.

[0026] In summary, the technical solution of the present invention has the following beneficial effects: 1. By setting θ e -5°≤θ j ≤θ e Within a range of +15°, the air inlet of the first vertical channel is accurately positioned within the area of ​​the first obliquely cut exhaust port in spatial projection, forming a continuous airflow channel. This design avoids misalignment or interference caused by excessive angular deviation, and achieves airflow connectivity without the need for additional structures, thus ensuring smooth air intake and reliable sealing.

[0027] 2. By setting θ e -5°≤θ j ≤θ e A range of +15° can significantly reduce the clearance volume of the intake passage, improve air intake efficiency, and allow the intake passage to be arranged along an optimal path. The path length and cross-sectional changes are limited to a minimum, thereby effectively reducing the clearance volume (i.e., the airflow stagnation or vortex region). This helps to reduce the amount of air intake remaining at the intake end, increase the actual intake volume of the cylinder, and thus improve efficiency and performance.

[0028] 3. By setting θ e -5°≤θ j ≤θ e A range of +15° optimizes the structural dimensions of the valve seat, facilitating layout and avoiding issues of excessive length or shortness. This value avoids extreme angles, ensuring a harmonious dimensional ratio between the height and radial directions of the first air-replenishing valve seat: it prevents the first air-replenishing valve seat from being too short due to a large angle, affecting the sealing surface length or structural strength; nor does it prevent insufficient sealing distance due to a small angle (e.g., exceeding -5°), encroaching on the space of other components. Ultimately, this achieves a compact and stable arrangement of the first air-replenishing valve seat within a limited space, reducing manufacturing difficulty. Attached Figure Description

[0029] Figure 1 This is a schematic diagram of the first cylinder in Embodiment 1 of this application; Figure 2 This is a schematic diagram of the first cylinder in Embodiment 1 of this application; Figure 3 This is a partial schematic diagram of the compressor in Embodiment 1 of this application; Figure 4 for Figure 3 Enlarged view of point A in the middle; Figure 5 for Figure 3 Enlarged view of point A in the middle; Figure 6 This is a schematic diagram of the first cylinder at other α angles in Embodiment 1 of this application; Figure 7This is a schematic diagram of the first cylinder of other Bc cylinders in Embodiment 1 of this application; Figure 8 This is a partial schematic diagram of the compressor in Embodiment 1 of this application; Figure 9 This is a partial schematic diagram of the compressor in Embodiment 1 of this application; Figure 10 This is a schematic diagram of the first cylinder in Embodiment 2 of this application; Figure 11 This is a schematic diagram of the first cylinder in Embodiment 2 of this application; Figure 12 This is a schematic diagram of the second cylinder in Embodiment 2 of this application; Figure 13 This is a schematic diagram of the second cylinder in Embodiment 2 of this application; Figure 14 This is a schematic diagram of a first cylinder with other α angles and a second cylinder with other β angles in Embodiment 2 of this application; Figure 15 This is a schematic diagram of the first cylinder of other Bc and the second cylinder of other Bn in Embodiment 2 of this application; Figure 16 This is a partial schematic diagram of the compressor in Embodiment 2 of this application; Figure 17 for Figure 16 Enlarged view at point B in the middle; Figure 18 for Figure 16 Enlarged view at point B in the middle; Figure 19 for Figure 16 Enlarged view at point C; Figure 20 for Figure 16 Enlarged view at point C; Figure 21 This is a partial schematic diagram of the compressor in Embodiment 2 of this application.

[0030] Explanation of reference numerals in the attached drawings: 1. First cylinder; 11. First air supply channel; 111. First transverse channel; 1111. Fifth plane; 112. First vertical channel; 1121. Central axis of the first vertical channel; 12. First exhaust oblique cut; 121. Central axis of the first exhaust oblique cut; 13. First vane groove; 131. Central axis of the first vane groove; 14. First plane; 15. Second plane; 16. Third plane; 17. Central axis of the first cylinder; 2. Upper bearing; 21. First clearance hole; 3. Lower bearing; 31. Second clearance hole; 4. First jet enthalpy enhancement assembly; 41. First air supply valve seat; 42. First air supply valve plate; 43. First limiter; 44. First locking screw; 45, Fourth plane; 5, Second cylinder; 51, Second air supply channel; 511, Second transverse channel; 5111, Tenth plane; 512, Second vertical channel; 5121, Central axis of the second vertical channel; 52, Second exhaust oblique cut; 521, Central axis of the second exhaust oblique cut; 53, Second sliding vane groove; 531, Central axis of the second sliding vane groove; 54, Sixth plane; 55, Seventh plane; 56, Eighth plane; 57, Central axis of the second cylinder; 6, Second jet enthalpy enhancement assembly; 61, Second air supply valve seat; 62, Second air supply valve plate; 63, Second limiter; 64, Second locking screw; 65, Ninth plane; 7, Intermediate partition; θ j The angle between the first plane and the second plane; θ e α, the angle between the third plane and the second plane; θp, the angle between the fourth plane and the first plane; Dc, the first inner diameter; Bc, the maximum sealing outer diameter of the upper bearing; Lj, the first projected length; θh, the angle between the sixth plane and the seventh plane; θi, the angle between the eighth plane and the seventh plane; β, the angle between the ninth plane and the sixth plane; θq, the angle between the tenth plane and the seventh plane; Dm, the second inner diameter; Bn, the maximum sealing outer diameter of the lower bearing; Lk, the second projected length; La, the limiting stroke of the first limiter on the first air supply valve plate; Lb, the limiting stroke of the second limiter on the second air supply valve plate; Y, the horizontal width at the connection between the first vertical channel and the first exhaust oblique cut or the horizontal width at the connection between the second vertical channel and the second exhaust oblique cut. Detailed Implementation

[0031] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0032] As attached Figure 1-9As shown (where Figure 3 and Figure 8 and Figure 9 (These are cross-sectional views of the compressor from different angles). Embodiment 1 of the present invention discloses a compressor including a first cylinder 1, an upper bearing 2, a lower bearing 3, and a first jet enthalpy enhancement assembly 4. The compressor is a single-cylinder compressor.

[0033] The first cylinder 1 is disposed between the upper bearing 2 and the lower bearing 3. The first cylinder 1 has a first cylinder central axis 17. The first cylinder 1 is provided with a first air supply channel 11, a first exhaust oblique cut 12 and a first sliding vane groove 13. The first air supply channel 11 includes a first transverse channel 111 and a first vertical channel 112. The first vertical channel 112 has a first vertical channel central axis 1121. The first exhaust oblique cut 12 has a first exhaust oblique cut central axis 121. The first sliding vane groove 13 has a first sliding vane groove central axis 131.

[0034] The first jet enthalpy enhancement assembly 4 is disposed on the upper end face of the first cylinder 1. The first jet enthalpy enhancement assembly 4 includes a first air supply valve seat 41, a first air supply valve plate 42, a first limiter 43 and a first locking screw 44 installed in the first air supply valve seat 41.

[0035] When the first air supply valve plate 42 covers the first air supply channel 11 (specifically the first vertical channel 112), the first air supply channel 11 and the first exhaust oblique cut 12 are in a non-connected state. When the first air supply valve plate 42 is not covered on the first air supply channel 11 (specifically the first vertical channel 112), the first air supply channel 11 and the first exhaust oblique cut 12 are in a connected state.

[0036] The first locking screw 44 passes through the first limiter 43 and the first air supply valve plate 42, and is threadedly connected to the first air supply valve seat 41 by the first locking screw 44. The plane formed between the central axis 1121 of the first vertical channel and the central axis 17 of the first cylinder is defined as the first plane 14, and the plane formed between the central axis 131 of the first sliding groove and the central axis 17 of the first cylinder is defined as the second plane 15. The first plane 14 and the second plane 15 have an included angle θ. j The plane formed between the central axis 121 of the first exhaust oblique cut and the central axis 17 of the first cylinder is defined as the third plane 16, and the third plane 16 has an included angle θ with the second plane 15. e θ j With θ e Satisfy the following relationship: θ e -5°≤θ j ≤θ e +15°, further, θ j With θ e Satisfying θ j =θ eIn this embodiment, θ j Take 12°, θ e Take 12°.

[0037] The first cylinder 1 has a first inner diameter Dc, the upper bearing 2 has a maximum sealing outer diameter Bc, and the first jet enthalpy enhancement component 4 is disposed within the sealing ring between the first inner diameter and the maximum sealing outer diameter of the upper bearing (i.e., disposed within the mating surface of the first cylinder 1 and the upper bearing 2). The first jet enthalpy enhancement component 4 has a first projected length Lj in the horizontal direction. Dc, Bc, and Lj satisfy 0.7*(Bc-Dc) / 2≤Lj≤1.3*(Bc-Dc) / 2. In this embodiment, Bc is 110mm, Dc is 60mm, and Lj is 110mm. j Take 25mm.

[0038] like Figure 7 As shown, the maximum sealing outer diameter Bc of the upper bearing can have multiple values, as long as the first jet enthalpy enhancement component 4 is set between the first inner diameter and the maximum sealing outer diameter of the upper bearing.

[0039] The head of the first locking screw 44 protrudes above the upper end face of the first cylinder 1. The upper bearing 2 has a first clearance hole 21 corresponding to the position of the head of the first locking screw 44. The first clearance hole 21 is a countersunk hole or a blind hole. The depth of the first clearance hole 21 is not less than the height of the head of the first locking screw 44 above the upper end face of the first cylinder 1 (a gap of 0.1mm-0.3mm is left between the inner wall of the first clearance hole 21 and the head of the first locking screw 44). In this embodiment, it is 0.2mm.

[0040] The symmetry center plane of the first jet enthalpy enhancement component 4 is defined as the fourth plane 45. The fourth plane 45 and the first plane 14 have an included angle α, which satisfies 0°≤α≤65°. Further, the included angle α satisfies 20°≤α≤55°. In this embodiment, 45° is taken.

[0041] like Figure 6 As shown, the included angle α between the fourth plane 45 and the first plane 14 can have multiple values, as long as the first jet enthalpy enhancement component 4 is set between the first inner diameter and the maximum sealing outer diameter of the upper bearing.

[0042] The symmetry center plane of the first transverse channel 111 is defined as the fifth plane 1111, and the fifth plane 1111 and the second plane 15 have an included angle θp, θ j With θ p Satisfy: θ p =θ j +8° or θ p =θ j -8°, further, θ p With θ j Satisfy: θ p =θj In this embodiment, θ p Take 20°.

[0043] The first air replenishment valve plate 42 is a reed valve plate. The first limiter 43 limits the first air replenishment valve plate 42 by a stroke of La. The value range of La is 0.5mm≤La≤2.5mm. In this embodiment, it is 1.2mm.

[0044] The theoretical displacement of the compressor is X (unit: cc), and the horizontal width at the junction of the first vertical channel 112 and the first exhaust oblique cut 12 is Y (unit: mm). X and Y satisfy Y=k* Where k takes values ​​in the range of 0.52≤k≤0.68, X takes values ​​in the range of 55≤X≤75, and Y takes values ​​in the range of 4≤Y≤6. In this embodiment, K is 0.67, X is 55, and Y is 5.

[0045] The beneficial effects of this embodiment 1 are as follows: 1. Significantly reduce processing costs: The first jet enthalpy enhancement component is set in the bearing sealing ring of the corresponding cylinder (the first jet enthalpy enhancement component is set between the first inner diameter and the maximum sealing outer diameter of the upper bearing). Standard flat partitions can be used instead of irregular partitions, reducing partition processing costs by more than 30%.

[0046] 2. Improved energy efficiency: The first jet enthalpy enhancement component is located close to the exhaust side, reducing the clearance volume by 3% to 5%, which can improve the compressor volumetric efficiency by 0.5% to 1.5% and the COP (coefficient of performance) by 1% to 2%.

[0047] 3. Effective noise reduction: After deducting the volume of the air supply valve and limiter, the internal cavity of the first jet enthalpy enhancement component forms a Helmholtz resonance silencing structure with the exhaust oblique cut. This structure can match the exhaust pulsation frequency of the compressor, and the noise reduction of the compressor can reach 2~3dB(A), solving the problem of prominent exhaust and jet noise.

[0048] 4. Achieve universal application: Breaking the limitation of existing technologies where the jet enthalpy enhancement structure is only compatible with dual-cylinder compressors, it can be directly applied to single-cylinder compressors, thus expanding the application scenarios of jet enthalpy enhancement technology.

[0049] Helmholtz resonance noise reduction structure (brief explanation) 1. Basic components: The sound-absorbing structure consists of a cavity and a short tube (or opening) connecting the cavity to the outside, resembling a "bottle".

[0050] 2. Noise reduction principle: It can be viewed as a "spring-mass" system: the air column inside the short tube acts as the "mass," vibrating back and forth in response to external sound waves. The air inside the cavity acts as the "spring," providing restoring force to the air column. When the frequency of external noise matches the natural frequency of this system, the air column vibrates violently, absorbing a large amount of sound energy at that frequency (converting it into heat), thus significantly reducing the noise at that frequency.

[0051] 3. Main features: Advantages: Simple structure, low pressure loss, and excellent noise reduction effect at the target frequency.

[0052] Example 2: As attached Figure 10 - Appendix Figure 21 As shown (where Figure 16 and Figure 21 (These are cross-sectional views of the compressor from different angles). Embodiment 2 of the present invention discloses a compressor including a first cylinder 1, an upper bearing 2, a lower bearing 3, a first jet enthalpy enhancement assembly 4, a second jet enthalpy enhancement assembly 6, an intermediate partition 7, and a second cylinder 5. The upper bearing 2, the first cylinder 1, the intermediate partition 7, the second cylinder 5, and the lower bearing 3 are arranged sequentially. This compressor is a dual-cylinder compressor.

[0053] The first cylinder 1 is disposed between the upper bearing 2 and the lower bearing 3. The first cylinder 1 has a first cylinder central axis 17. The first cylinder 1 is provided with a first air supply channel 11, a first exhaust oblique cut 12 and a first sliding vane groove 13. The first air supply channel 11 includes a first transverse channel 111 and a first vertical channel 112. The first vertical channel 112 has a first vertical channel central axis 1121. The first exhaust oblique cut 12 has a first exhaust oblique cut central axis 121. The first sliding vane groove 13 has a first sliding vane groove central axis 131.

[0054] The first jet enthalpy enhancement assembly 4 is disposed on the upper end face of the first cylinder 1. The first jet enthalpy enhancement assembly 4 includes a first air supply valve seat 41, a first air supply valve plate 42, a first limiter 43 and a first locking screw 44 installed in the first air supply valve seat 41.

[0055] When the first air supply valve plate 42 covers the first air supply channel 11 (specifically the first vertical channel 112), the first air supply channel 11 and the first exhaust oblique cut 12 are in a non-connected state. When the first air supply valve plate 42 is not covered on the first air supply channel 11 (specifically the first vertical channel 112), the first air supply channel 11 and the first exhaust oblique cut 12 are in a connected state.

[0056] The first locking screw 44 passes through the first limiter 43 and the first air supply valve plate 42, and is threadedly connected to the first air supply valve seat 41 by the first locking screw 44. The plane formed between the central axis 1121 of the first vertical channel and the central axis 17 of the first cylinder is defined as the first plane 14, and the plane formed between the central axis 131 of the first sliding groove and the central axis 17 of the first cylinder is defined as the second plane 15. The first plane 14 and the second plane 15 have an included angle θ. j The plane formed between the central axis 121 of the first exhaust oblique cut and the central axis 17 of the first cylinder is defined as the third plane 16, and the third plane 16 has an included angle θ with the second plane 15. e θ j With θ e Satisfy the following relationship: θ e -5°≤θ j ≤θ e +15°, further, θ j With θ e Satisfying θ j =θ e In this embodiment, θ j Take 12°, θ e Take 12°.

[0057] The second cylinder 5 has a second cylinder central axis 57. The second cylinder 5 is provided with a second air supply channel 51, a second exhaust oblique cut 52 and a second sliding vane groove 53. The second air supply channel 51 includes a second horizontal channel 511 and a second vertical channel 512. The second vertical channel 512 has a second vertical channel central axis 5121. The second exhaust oblique cut 52 has a second exhaust oblique cut central axis 521. The second sliding vane groove 53 has a second sliding vane groove central axis 531.

[0058] The second jet enthalpy enhancement assembly 6 is disposed on the lower end face of the second cylinder 5. The second jet enthalpy enhancement assembly 6 includes a second air supply valve seat 61, a second air supply valve plate 62, a second limiter 63 and a second locking screw 64 installed in the second air supply valve seat 61.

[0059] When the second air supply valve plate 62 covers the second air supply channel 51 (specifically the second vertical channel 512), the second air supply channel 51 and the second exhaust oblique cut 52 are in a non-connected state. When the second air supply valve plate 62 is not covered on the second air supply channel 51 (specifically the second vertical channel 512), the second air supply channel 51 and the second exhaust oblique cut 52 are in a connected state.

[0060] The second locking screw 54 passes through the second limiter 63 and the second air supply valve plate 62 and is threadedly connected to the second air supply valve seat 61 by the second locking screw 54. The plane formed between the second vertical channel center axis 5121 and the second cylinder center axis 57 is defined as the sixth plane 54. The plane formed between the second sliding plate groove center axis 531 and the second cylinder center axis 57 is defined as the seventh plane 55. The sixth plane 54 and the seventh plane 55 have an included angle θh. The plane formed between the second exhaust oblique cut center axis 521 and the second cylinder center axis 57 is defined as the eighth plane 56. The eighth plane 56 and the seventh plane 55 have an included angle θi. θh and θi satisfy the following relationship: θi-5°≤θh≤θi+15°. Further, θh and θi satisfy θh=θi. In this embodiment, θi is 12° and θh is 12°.

[0061] The first cylinder 1 has a first inner diameter Dc, and the upper bearing has a maximum sealing outer diameter Bc. The first jet enthalpy enhancement component 4 is disposed within the sealing ring between the first inner diameter and the maximum sealing outer diameter of the upper bearing (i.e., disposed on the contact surface between the first cylinder 1 and the upper bearing 2). The first jet enthalpy enhancement component 4 has a first projected length Lj in the horizontal direction. Dc, Bc, and Lj satisfy 0.7*(Bc-Dc) / 2≤Lj≤1.3*(Bc-Dc) / 2. In this embodiment, Bc is 110mm, Dc is 60mm, and Lj is 110mm. j Take 25mm.

[0062] The second cylinder 5 has a second inner diameter Dm, the lower bearing 3 has a maximum sealing outer diameter Bn, and the second jet enthalpy enhancement component 6 is disposed in the sealing ring between the second inner diameter and the maximum sealing outer diameter of the lower bearing (that is, disposed on the contact surface between the second cylinder 5 and the lower bearing 3). The second jet enthalpy enhancement component 6 has a second projected length Lk in the horizontal direction. Dm, Bn, and Lk satisfy 0.7*(Bn-Dm) / 2≤Lk≤1.3*(Bn-Dm) / 2. In this embodiment, Bn is 110mm, Dm is 60mm, and Lk is 25mm.

[0063] like Figure 15 As shown, the maximum sealing outer diameter Bc of the upper bearing and the maximum sealing outer diameter Bn of the lower bearing can have various values, as long as the first jet enthalpy enhancement component 4 is set between the first inner diameter and the maximum sealing outer diameter of the upper bearing, and the second jet enthalpy enhancement component 6 is set between the second inner diameter and the maximum sealing outer diameter of the lower bearing.

[0064] The head of the first locking screw 44 protrudes above the upper end face of the first cylinder 1. The upper bearing 2 has a first clearance hole 21 corresponding to the position of the head of the first locking screw 44. The first clearance hole 21 is a countersunk hole or a blind hole. The depth of the first clearance hole 21 is not less than the height of the head of the first locking screw 44 above the upper end face of the first cylinder 1 (a gap of 0.1mm-0.3mm is left between the inner wall of the first clearance hole 21 and the head of the first locking screw 44). In this embodiment, it is 0.2mm.

[0065] The head of the second locking screw 64 protrudes above the lower end face of the second cylinder 5. The lower bearing 3 has a second clearance hole 31 corresponding to the position of the head of the second locking screw 64. The second clearance hole 31 is a countersunk hole or a blind hole. The depth of the second clearance hole 31 is not less than the height of the head of the second locking screw 64 above the lower end face of the second cylinder 5 (a gap of 0.1mm-0.3mm is left between the inner wall of the second clearance hole 31 and the head of the second locking screw 64). In this embodiment, it is 0.2mm.

[0066] The symmetry center plane of the first jet enthalpy enhancement component 4 is defined as the fourth plane 45. The fourth plane 45 and the first plane 14 have an included angle α, which satisfies 0°≤α≤65°. Further, the included angle α satisfies 20°≤α≤55°. In this embodiment, 45° is taken.

[0067] The symmetry center plane of the second jet enthalpy enhancement component 6 is defined as the ninth plane 65. The ninth plane 65 and the sixth plane 54 have an included angle β, which satisfies 0°≤β≤65°. Furthermore, the included angle β satisfies 20°≤β≤55°. In this embodiment, it is taken as 45°.

[0068] like Figure 14 As shown, the angle α between the fourth plane 45 and the first plane 14 and the angle β between the ninth plane 65 and the sixth plane 54 can have various values, as long as the first jet enthalpy enhancement component 4 is set between the first inner diameter and the maximum sealing outer diameter of the upper bearing, and the second jet enthalpy enhancement component 6 is set between the second inner diameter and the maximum sealing outer diameter of the lower bearing.

[0069] The symmetry center plane of the first transverse channel 111 is defined as the fifth plane 1111, and the fifth plane 1111 and the second plane 15 have an included angle θp, θ j With θ p Satisfy: θ p =θ j +8° or θ p =θ j -8°, further, θ p With θ j Satisfy: θ p =θ j In this embodiment, θ p Take 20°.

[0070] The symmetry center plane of the second transverse channel 511 is defined as the tenth plane 5111. The tenth plane 51111 and the seventh plane 55 have an angle θq between them. θq and θh satisfy: θq=θh+8° or θq=θh-8°. Furthermore, θq and θh satisfy: θq=θh. In this embodiment, θq is taken as 20°.

[0071] The first air replenishment valve plate 42 is a reed valve plate. The first limiter 43 limits the first air replenishment valve plate 42 by a stroke of La. The value range of La is 0.5mm≤La≤2.5mm. In this embodiment, it is 1.2mm.

[0072] The second air supply valve plate 62 is a reed valve plate. The second limiter 63 limits the travel of the second air supply valve plate 62 to Lb. The value range of Lb is: 0.5mm≤Lb≤2.5mm. In this embodiment, it is 1.2mm.

[0073] The theoretical displacement of the compressor is X (unit: cc). The horizontal width at the junction of the first vertical channel 112 and the first exhaust oblique cut 12 and the horizontal width at the junction of the second vertical channel 512 and the second exhaust oblique cut 52 are both Y (unit: mm). X and Y satisfy Y=k* Where k takes values ​​in the range of 0.52≤k≤0.68, X takes values ​​in the range of 55≤X≤75, and Y takes values ​​in the range of 4≤Y≤6. In this embodiment, K is 0.67, X is 55, and Y is 5.

[0074] The beneficial effects of this embodiment 2 are as follows: 1. Significantly reduce processing costs: The first jet enthalpy enhancement component and the second jet enthalpy enhancement component are respectively set in the bearing sealing ring of the corresponding cylinder (the first jet enthalpy enhancement component is set between the first inner diameter and the maximum sealing outer diameter of the upper bearing, and the second jet enthalpy enhancement component is set between the second inner diameter and the maximum sealing outer diameter of the lower bearing). Standard flat partitions can be used to replace irregular partitions, reducing partition processing costs by more than 30%.

[0075] 2. Improved energy efficiency: The first and second jet enthalpy enhancement components are located close to the exhaust side, reducing the clearance volume by 3% to 5%, which can improve the compressor volumetric efficiency by 0.5% to 1.5% and the COP (coefficient of performance) by 1% to 2%.

[0076] 3. Effective noise reduction: After deducting the volume of their respective supplementary air valves and limiters, the internal cavities of the first and second jet enthalpy enhancement components, together with their respective exhaust oblique cutouts, form Helmholtz resonance silencing structures. This structure can match the compressor exhaust pulsation frequency, achieving a noise reduction of 2-3 dB(A) for both single-cylinder and dual-cylinder compressors, thus solving the problem of prominent exhaust and jet noise. The description of the Helmholtz resonance silencing structure is consistent with that in Example 1.

[0077] The above are all preferred embodiments of the present invention and are not intended to limit the scope of protection of the present invention. Therefore, all equivalent changes made in accordance with the structure, shape and principle of the present invention should be covered within the scope of protection of the present invention.

Claims

1. A compressor, characterized in that: The compressor includes a first cylinder, an upper bearing, and a lower bearing. The first cylinder is disposed between the upper bearing and the lower bearing. The first cylinder has a first cylinder central axis. The first cylinder is provided with a first air supply channel, a first exhaust oblique cut, and a first sliding vane groove. The first air supply channel includes a first transverse channel and a first vertical channel. The first vertical channel has a first vertical channel central axis. The first exhaust oblique cut has a first exhaust oblique cut central axis. The first sliding vane groove has a first sliding vane groove central axis. The compressor also includes a first jet enthalpy enhancement assembly. The first jet enthalpy enhancement assembly is disposed on the upper end face of the first cylinder. The first jet enthalpy enhancement assembly includes a first air supply valve seat, a first air supply valve plate, a first limiter, and a first locking screw installed in the first air supply valve seat. When the first air replenishment valve plate is closed on the first air replenishment channel, the first air replenishment channel and the first exhaust oblique cut are in a non-connected state; when the first air replenishment valve plate is not closed on the first air replenishment channel, the first air replenishment channel and the first exhaust oblique cut are in a connected state. The first locking screw passes through the first limiter and the first air supply valve plate, and is threadedly connected to the first air supply valve seat via the first locking screw. The plane formed between the central axis of the first vertical channel and the central axis of the first cylinder is defined as the first plane, and the plane formed between the central axis of the first sliding groove and the central axis of the first cylinder is defined as the second plane. The first plane and the second plane have an included angle θ. j ; The plane formed between the central axis of the first exhaust oblique cut and the central axis of the first cylinder is defined as the third plane, and the third plane has an angle θ with the second plane. e ; The θ j With the θ e Satisfy the following relationship: θ e -5°≤θ j ≤θ e +15°.

2. The compressor according to claim 1, characterized in that: The θ j With the θ e Satisfying θ j =θ e .

3. The compressor according to claim 1, characterized in that: The first cylinder has a first inner diameter, the upper bearing has a maximum sealing outer diameter, and the first jet enthalpy enhancement component is disposed between the first inner diameter and the maximum sealing outer diameter of the upper bearing. The first inner diameter is Dc, the maximum sealing outer diameter of the upper bearing is Bc, and the first jet enthalpy enhancement component has a first projected length Lj in the horizontal direction. The Dc, Bc, and Lj satisfy 0.7*(Bc-Dc) / 2≤Lj≤1.3*(Bc-Dc) / 2.

4. The compressor according to claim 1, characterized in that: The head of the first locking screw is higher than the upper end face of the first cylinder. The upper bearing has a first clearance hole at the position corresponding to the head of the first locking screw. The depth of the first clearance hole is not less than the height of the head of the first locking screw above the upper end face of the first cylinder.

5. The compressor according to claim 4, characterized in that: The first clearance hole is a countersunk hole or a blind hole, and there is a gap of 0.1mm-0.3mm between the inner wall of the first clearance hole and the head of the first locking screw.

6. The compressor according to claim 1, characterized in that: The symmetry center plane of the first jet enthalpy enhancement component is defined as the fourth plane, and the fourth plane has an angle α with the first plane, the angle α satisfying 0°≤α≤65°.

7. The compressor according to claim 6, characterized in that: The included angle α satisfies 20°≤α≤55°.

8. The compressor according to claim 1, characterized in that: The symmetry center plane of the first transverse channel is defined as the fifth plane, which has an angle θp with the second plane. j With the θ p Satisfy: θ p =θ j +8° or θ p =θ j -8°.

9. The compressor according to claim 8, characterized in that: The θ p With the θ j Satisfy: θ p =θ j .

10. The compressor according to claim 1, characterized in that: The first air replenishment valve is a reed valve, and the first limiter limits the first air replenishment valve by a stroke of La, wherein the value of La is 0.5mm≤La≤2.5mm.

11. The compressor according to claim 1, characterized in that: The compressor also includes an intermediate partition and a second cylinder, and the upper bearing, the first cylinder, the intermediate partition, the second cylinder, and the lower bearing are arranged in sequence. The second cylinder has a second cylinder central axis, and the second cylinder is provided with a second air supply channel, a second exhaust oblique cut, and a second sliding vane groove. The second air supply channel includes a second transverse channel and a second vertical channel. The second vertical channel has a second vertical channel central axis. The second exhaust oblique cut has a second exhaust oblique cut central axis. The second sliding vane groove has a second sliding vane groove central axis. It also includes a second jet enthalpy enhancement assembly. The second jet enthalpy enhancement assembly is disposed on the lower end face of the second cylinder. The second jet enthalpy enhancement assembly includes a second air supply valve seat, a second air supply valve plate, a second limiter, and a second locking screw installed in the second air supply valve seat. When the second air supply valve plate is closed on the second air supply channel, the second air supply channel and the second exhaust oblique cut are in a non-connected state; when the second air supply valve plate is not closed on the second air supply channel, the second air supply channel and the second exhaust oblique cut are in a connected state. The second locking screw passes through the second limiter and the second air supply valve plate and is threadedly connected to the second air supply valve seat through the second locking screw. The plane formed between the central axis of the second vertical channel and the central axis of the second cylinder is defined as the sixth plane. The plane formed between the central axis of the second sliding plate groove and the central axis of the second cylinder is defined as the seventh plane. The sixth plane and the seventh plane have an included angle θh. The plane formed between the central axis of the second exhaust oblique cut and the central axis of the second cylinder is defined as the eighth plane, and the eighth plane has an included angle θi with the seventh plane; The relationship between θh and θi is as follows: θi-5°≤θh≤θi+15°.

12. The compressor according to claim 11, characterized in that: The θh and θi satisfy θh=θi.

13. The compressor according to claim 11, characterized in that: The second cylinder has a second inner diameter, the lower bearing has a maximum sealing outer diameter, the second jet enthalpy enhancement assembly is disposed between the second inner diameter and the maximum sealing outer diameter of the lower bearing, the second inner diameter is Dm, the maximum sealing outer diameter of the lower bearing is Bn, the second jet enthalpy enhancement assembly has a second projected length Lk in the horizontal direction, and Dm, Bn, and Lk satisfy 0.7*(Bn-Dm) / 2≤Lk≤1.3*(Bn-Dm) / 2.

14. The compressor according to claim 11, characterized in that: The head of the second locking screw is higher than the lower end face of the second cylinder. The lower bearing has a second clearance hole at the position corresponding to the head of the second locking screw. The depth of the second clearance hole is not less than the height of the head of the second locking screw above the lower end face of the second cylinder.

15. The compressor according to claim 14, characterized in that: The second clearance hole is a countersunk hole or a blind hole, and there is a gap of 0.1mm-0.3mm between the inner wall of the second clearance hole and the head of the second locking screw.

16. The compressor according to claim 11, characterized in that: The symmetry center plane of the second jet enthalpy enhancement component is defined as the ninth plane, and the ninth plane and the sixth plane have an included angle β, which satisfies 0°≤β≤65°.

17. The compressor according to claim 16, characterized in that: The included angle β satisfies 20°≤β≤55°.

18. The compressor according to claim 11, characterized in that: The symmetry center plane of the second transverse channel is defined as the tenth plane, and the tenth plane and the seventh plane have an angle θq between them. The θq and θh satisfy: θq=θh+8° or θq=θh-8°.

19. The compressor according to claim 18, characterized in that: The θq and θh satisfy the condition: θq = θh.

20. The compressor according to claim 11, characterized in that: The second air replenishment valve is a reed valve, and the limiting stroke of the second limiter on the second air replenishment valve is Lb, wherein the value range of Lb is: 0.5mm≤Lb≤2.5mm.

21. The compressor according to any one of claims 1-20, characterized in that: The theoretical displacement of the compressor is X, and the horizontal width at the junction of the first vertical channel and the first exhaust oblique cut, or the horizontal width at the junction of the second vertical channel and the second exhaust oblique cut, is Y. X and Y satisfy Y = k * The values ​​of k are in the range of 0.52≤k≤0.68, the values ​​of X are in the range of 55≤X≤75, and the values ​​of Y are in the range of 4≤Y≤6.

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