Compressor and HVAC apparatus

Abstract

The present application relates to a compressor and an HVAC apparatus. The compressor comprises a compressor housing and a pump body structure arranged inside the compressor housing. The pump body structure comprises an upper silencing cover, an upper bearing, a cylinder, a lower bearing and a lower silencing cover which are successively arranged in the axial direction; the upper silencing cover is provided with an air outlet; an upper silencing chamber is formed between the upper silencing cover and the upper bearing; a lower silencing chamber is formed between the lower silencing cover and the lower bearing; the lower bearing is provided with a lower exhaust through hole communicating the interior of the cylinder with the lower silencing chamber; a plurality of refrigerant channels communicating the upper silencing chamber and the lower silencing chamber penetrate through the upper bearing, the cylinder and the lower bearing in the axial direction; the cylinder comprises a cylinder body and a flange portion sleeved on the outer peripheral side of the cylinder body; and the flange portion is connected to the compressor housing. Compared with the prior art, the compressor and the HVAC apparatus of the present application have the advantages of improved energy efficiency and reduced noise.

Description

A compressor and heating and ventilation equipment Technical Field

[0001] This application relates to the field of compressor technology, and in particular to a compressor and heating and ventilation equipment. Background Technology

[0002] A typical compressor includes a compressor housing, a stator, a rotor, a crank, and a pump body. The stator is installed inside the compressor housing and sleeved on the outside of the rotor. The rotor drives the crank to rotate eccentrically within the cylinder of the pump body to compress the low-pressure gaseous refrigerant, turning it into a high-temperature, high-pressure gaseous refrigerant before it is discharged from the compressor.

[0003] Compressors are generally classified into single-cylinder and double-cylinder pump bodies based on the number of cylinders in their pump body. Single-cylinder pump bodies use an upper and lower exhaust method. When the refrigerant is discharged from the lower exhaust port of the cylinder, it needs to pass through the lower bearing into the lower muffler cover, and then through the channel that runs through the lower bearing, cylinder, and upper bearing into the upper muffler cover, and finally be discharged out of the pump body.

[0004] However, during use, it has been found that compressors using single-cylinder pump bodies generally suffer from technical problems such as large heat exchange losses and low energy efficiency, resulting in poor working efficiency of existing compressors. Summary of the Invention

[0005] Based on this, the purpose of this application is to overcome the shortcomings of the prior art and provide a refrigerant compressor that can effectively reduce the input power and heat exchange loss during pump structure discharge, improve the energy efficiency of the refrigerant compressor, and reduce the noise of the refrigerant compressor. The technical solution is as follows:

[0006] Compressor housing; and

[0007] The pump body structure is located inside the compressor housing and includes at least one cylinder and at least two refrigeration channels; the refrigeration channels pass through the cylinder along its axial direction; the cylinder is fixed relative to the compressor housing.

[0008] In one embodiment, the pump body structure further includes an upper silencer cover, an upper bearing, a lower bearing, and a lower silencer cover arranged sequentially along the axial direction. The cylinder is located between the upper bearing and the lower bearing. The upper silencer cover has an air outlet, and an upper silencer cavity is formed between the upper silencer cover and the upper bearing. The lower silencer cover and the lower bearing form a lower silencer cavity. The lower bearing has a lower exhaust port that connects the interior of the cylinder and the lower silencer cavity. Each refrigerant passage passes through the upper bearing, the cylinder, and the lower bearing sequentially along the axial direction of the cylinder and connects the upper silencer cavity and the lower silencer cavity. The cylinder includes a cylinder body and a flange portion sleeved on the outer peripheral side of the cylinder body. The outer peripheral wall of the flange portion is connected to the inner peripheral wall of the compressor housing.

[0009] In one embodiment, the inner diameter of the compressor housing is D, and the discharge capacity of the pump structure is V. The relationship between V and D is: 4V / πD. 2 ≥1.2mm.

[0010] In one embodiment, the inner diameter of the lower exhaust port is L, the number of refrigerant channels is n, and the inner diameter of each refrigerant channel is d. The relationship between d, n, and L is: 2 ≤ n * d 2 / L 2 ≤4.

[0011] Therefore, in the compressor according to the embodiment of the present invention, the relationship between the inner diameter L of the lower exhaust port of the pump body structure and the number n and inner diameter d of the refrigerant channels is designed to be 2≤n*d. 2 / L 2 ≤4 ensures that the refrigerant discharged from the lower exhaust port has sufficient space to smoothly discharge into the upper silencer chamber after entering the lower silencer chamber. This effectively improves the exhaust resistance of the pump body structure, reduces the heat exchange loss of the compressor, and relatively reduces the required power input, thereby effectively improving the energy efficiency of the compressor.

[0012] In one embodiment, the upper bearing and the lower bearing are respectively disposed on the upper and lower end faces of the cylinder body, and the refrigerant channel passes through the upper bearing, the cylinder body and the lower bearing in sequence; the cylinder body is provided with a compression chamber inside, and the radial width of the cylinder body is t, wherein t and d satisfy the relationship: 2≤t / d≤2.5.

[0013] Therefore, in the compressor according to the embodiment of the present invention, by designing the relationship between the inner diameter d of the refrigerant passage and the radial width t of the cylinder body as 2≤t / d≤2.5, a certain sealing distance is ensured between the refrigerant passage and both the inner and outer sides of the cylinder body. In this way, the risk of refrigerant leakage in the refrigerant passage can be effectively reduced, while ensuring that the refrigerant in the refrigerant passage has sufficient passage space to be smoothly discharged into the upper silencer cavity, thereby effectively improving the efficiency of the compressor.

[0014] In one embodiment, the diameter of the upper bearing is greater than or equal to the diameter of the cylinder body, and the diameter of the upper bearing is smaller than the diameter of the flange; the diameter of the lower bearing is greater than or equal to the diameter of the cylinder body, and the diameter of the lower bearing is smaller than the diameter of the flange. It can be understood that in this embodiment of the invention, the cylinder is connected and fixed to the inner circumference of the compressor housing via the outer periphery of the flange, while the upper and lower bearings respectively cover the upper and lower end faces of the cylinder body. Due to the connection between the cylinder and the housing, the natural frequency of the pump structure is improved, resulting in noise reduction.

[0015] In one embodiment, several refrigerant channels are spaced apart along the circumference of the cylinder body, and bolt channels are provided on both sides of each refrigerant channel. The bolt channels pass through the upper muffler cover, the upper bearing, the cylinder body, the lower bearing, and the lower muffler cover in sequence.

[0016] In one embodiment, the upper end face of the cylinder body is provided with an upper exhaust notch communicating with the compression chamber, and the upper bearing is provided with an upper exhaust valve seat communicating with the upper exhaust notch and the upper muffler chamber; the lower end face of the cylinder body is provided with a lower exhaust notch communicating with the compression chamber, and the lower bearing is provided with a lower exhaust valve seat communicating with the lower exhaust notch, and the lower exhaust through hole is communicating with the lower exhaust valve seat.

[0017] As one embodiment, it also includes a crankshaft, wherein the upper muffler cover, the upper bearing, the cylinder body, the lower bearing, and the lower muffler cover are sequentially inserted through the crankshaft.

[0018] In one embodiment, the flange is an annular structure, and several oil return channels are provided through the flange along the axial direction. These oil return channels are spaced apart along the circumference of the flange. It can be understood that, in this embodiment of the cylinder, by providing oil return channels on the flange, the lubricating oil falls back to the bottom of the pump body structure, ensuring that the oil level inside the compressor housing is at a certain height.

[0019] In one embodiment, the compressor housing is a sealed container for storing refrigeration oil, and an electric component is housed inside the compressor housing for driving the pump structure to compress the refrigerant.

[0020] As one implementation, the refrigerant compressed by the pump body structure is at least a natural refrigerant, an HFC refrigerant, or an HFO refrigerant.

[0021] In one embodiment, the natural refrigerant is at least one of R290 and CO2, or a mixture thereof; the HFC refrigerant is at least one of R32, R410A, R134a, R404A, and R407C, or a mixture thereof; and the HFO refrigerant is at least one of R454B, R454C, R513A, and R1234yf, or a mixture thereof.

[0022] In one embodiment, the refrigeration oil is at least one of POE oil and PVE oil, or a mixture thereof.

[0023] In one implementation, the relationship between d, n, and L is: n*d 2 / L 2 =3.

[0024] In one implementation, t and d satisfy the relationship: t / d = 2.3.

[0025] In one embodiment, the axial height of the cylinder along the compressor housing is H, and H and D satisfy the relationship: D / H < 4.5.

[0026] As one embodiment, the compressor of this application further includes:

[0027] The stator has a connecting part and a recessed part on its outer peripheral side. The connecting part is connected to the inner peripheral wall of the compressor housing, and the recessed part is in clearance fit with the inner peripheral wall of the compressor housing.

[0028] The rotor is coaxially disposed inside the stator, and the rotor and the stator form a clearance fit;

[0029] The pump body structure is located below the stator and the rotor, and the rotor is drivenly connected to the pump body structure;

[0030] The pump body structure has a discharge capacity of V, the gap area formed between the recess and the compressor housing is S1, a first refrigerant channel is formed between the coil slot of the stator and the coil in the slot, the area of ​​the first refrigerant channel is S2, the gap area formed between the stator and the rotor is S3, a second refrigerant channel is provided in the rotor, the area of ​​the second refrigerant channel is S4, and the total area of ​​the compressor housing for refrigerant to pass through in the axial direction is S. The S satisfies the relationship: S=S1+S2+S3+S4; the V and the S satisfy the relationship: 10mm≤V / S≤15mm.

[0031] Therefore, according to the compressor of this application, by improving the structure of the stator and rotor, and limiting the ratio between the total area S of the stator, rotor and compressor housing for refrigerant passage and the discharge volume V of the pump body structure to 10mm≤V / S≤15mm, the iron loss of the compressor can be maintained on a good basis, while effectively reducing the discharge of refrigerant oil from the compressor. This reduces the amount of refrigerant oil discharged by the compressor, and the oil level of the pump body structure can be maintained at a normal level, effectively extending the service life of the pump body structure and the compressor. In addition, by providing a recessed part on the outer periphery of the stator, the contact area between the stator and the compressor housing is reduced, which can avoid the deformation caused by the stator being heat-fitted to the compressor housing through the joint.

[0032] In one embodiment, the inner diameter of the compressor housing is D, and V and D satisfy the relationship: 4V / πD 2 ≥1.2mm; where π is the mathematical constant pi.

[0033] In one embodiment, the pump body structure has a return oil channel extending through it in the axial direction. The area of ​​the return oil channel is S5. The relationship between S5 and V is: 8mm≤V / S5≤12mm; the relationship between S5 and S is: 0.7≤S / S5≤0.9.

[0034] This structural design ensures that the ratio between the area S5 of the oil return channel on the pump body structure and the discharge capacity V of the pump body structure is limited to 8mm≤V / S5≤12mm, guaranteeing smooth oil return in the pump body structure. Furthermore, the ratio between the area S5 of the oil return channel on the pump body structure and the total area S formed by the stator, rotor, and compressor housing for refrigerant passage is limited to 0.7≤S / S5≤0.9, effectively ensuring that the refrigeration oil level remains at a good level, allowing the oil level in the pump body structure to be maintained at a normal level, thus effectively extending the service life of the pump body structure and compressor.

[0035] In one embodiment, the upper bearing, the cylinder, and the lower bearing are coaxially arranged. The cylinder has a compression chamber with openings at both ends. The outer side wall of the cylinder is recessed in the radial direction to form an air intake channel communicating with the compression chamber. The upper bearing and the lower bearing are respectively located at the upper and lower openings of the compression chamber.

[0036] In one embodiment, the cylinder has several arc-shaped channels distributed along the circumferential direction, passing through both ends of the cylinder, and the several arc-shaped channels together form the oil return channel.

[0037] In one embodiment, a plurality of joint portions are evenly distributed on the outer periphery of the stator, and a recessed portion is provided between two adjacent joint portions. The recessed portion is formed by recessing inward from the outer periphery of the stator, and the arc length of the recessed portion in the circumferential direction is smaller than the arc length of the joint portion in the circumferential direction.

[0038] In one implementation, V and S satisfy the relationship: V / S = 12 mm.

[0039] In one implementation, S5 and V satisfy the following relationship: V / S5 = 10 mm; S5 and S satisfy the following relationship: S / S5 = 0.9.

[0040] In one embodiment, the upper bearing and the lower bearing are respectively disposed on the upper and lower end faces of the cylinder. The upper bearing has an upper through hole that communicates with the compression chamber in the axial direction, and the lower bearing has a lower through hole that communicates with the compression chamber in the axial direction.

[0041] The crankshaft includes a long shaft, an eccentric shaft, and a short shaft connected axially in sequence. The long shaft passes through the upper through hole, the eccentric shaft is disposed in the compression chamber, and the short shaft is disposed in the lower through hole. The shortest distance from the axis of the eccentric shaft to the axis of the long shaft is E, and the diameter of the short shaft is d1. E and d1 satisfy the relationship: E / d1≤0.35. The axial length of the eccentric shaft is H1, and the axial length of the short shaft is h. H1 and h satisfy the relationship: H1 / h≤1.2.

[0042] A rotating oil groove is recessed on the inner wall of the lower through hole. The two ends of the rotating oil groove respectively penetrate the two ends of the lower through hole. The radial cross-sectional area of ​​the rotating oil groove is S6. The relationship between S6 and d1 is: 0.05mm≤S6 / d1≤0.1mm.

[0043] Therefore, the compressor according to the embodiments of this application improves the structure of the eccentric shaft, short shaft, and lower bearing on the crankshaft, so that the shortest distance E from the axis of the eccentric shaft to the axis of the long shaft satisfies the relationship E / d1≤0.35 with the diameter d1 of the short shaft. This effectively reduces the load on the short shaft while ensuring the displacement. Furthermore, by providing a rotating oil groove on the inner wall of the lower through hole of the lower bearing, the radial cross-sectional area S6 of the rotating oil groove satisfies the relationship 0.05mm≤S6 / d1≤0.1mm with the diameter d1 of the short shaft. This allows the lubricating oil to flow more smoothly along the rotating oil groove to the inner wall of the lower through hole of the lower bearing, the eccentric shaft, and other components. It also facilitates the formation of an oil film between the short shaft and the lower bearing, effectively reducing wear between the short shaft and the lower bearing, preventing sintering between the short shaft and the lower bearing, and effectively improving the reliability of the compressor.

[0044] In one embodiment, the rotation angle of the rotating oil tank is θ, the height of the rotating oil tank is L1, and the relationship between L1 and θ is: 2° / mm≤θ / L1≤4° / mm.

[0045] Therefore, according to the compressor of this application embodiment, by ensuring that the rotation angle θ of the rotating oil groove and the height L1 of the rotating oil groove satisfy the relationship 2° / mm≤θ / L1≤4° / mm, the inclination of the rotating oil groove can be kept within a certain range, and the thickness of the oil film formed between the short shaft and the lower through hole can reach a relatively thick value, thereby effectively reducing the wear between the short shaft and the lower bearing, avoiding the sintering phenomenon between the short shaft and the lower bearing, and effectively improving the reliability of the compressor.

[0046] In one implementation, L1 and θ satisfy the relationship: θ / L1 = 3° / mm.

[0047] In one embodiment, the rotation direction of the rotating oil groove is opposite to the rotation direction of the short shaft.

[0048] Furthermore, this application also provides a heating and ventilation device including the compressor of any of the above embodiments. The heating and ventilation device according to embodiments of the present invention can effectively reduce the electrical input and heat exchange losses during pump body structure exhaust, thereby improving the energy efficiency of the refrigerant compressor. In addition, due to the connection between the cylinder and the housing, the natural frequency of the pump body structure is improved, which effectively reduces the noise of the refrigerant compressor.

[0049] To better understand and implement this invention, the following detailed description is provided in conjunction with the accompanying drawings. Attached Figure Description

[0050] Figure 1 is a schematic diagram of the overall structure of the compressor of this application;

[0051] Figure 2 is a cross-sectional view of the overall structure of the compressor of this application;

[0052] Figure 3 is a front view of the pump body structure of the compressor according to Embodiment 1 of this application;

[0053] Figure 4 is a top view of the pump body structure of the compressor according to Embodiment 1 of this application;

[0054] Figure 5 is a schematic cross-sectional view along direction AA shown in Figure 4;

[0055] Figure 6 is a top view of the compressor of Embodiment 1 of this application with the muffler cover removed from the pump body structure;

[0056] Figure 7 is an exploded view of the upper bearing, cylinder, and lower bearing of Embodiment 1 of this application;

[0057] Figure 8 is a simulation curve of the heat exchange loss of the compressor in Embodiment 1 of this application;

[0058] Figure 9 is a simulation diagram of the energy efficiency curve of the compressor in Embodiment 1 of this application;

[0059] Figure 10 is one of the structural schematic diagrams of the compressor in Embodiment 2 of this application;

[0060] Figure 11 is an enlarged schematic diagram of part B shown in Figure 10;

[0061] Figure 12 is a second schematic diagram of the compressor structure in Embodiment 2 of this application;

[0062] Figure 13 is a schematic diagram of the cylinder structure of the compressor in Embodiment 2 of this application;

[0063] Figure 14 is a graph showing the relationship between the oil quantity in the compressor housing and the stator iron loss in Embodiment 2 of this application;

[0064] Figure 15 is a graph showing the relationship between the oil level and V / S5 of the compressor in Embodiment 2 of this application;

[0065] Figure 16 is one of the schematic diagrams showing the connection between the crankshaft and the lower bearing in Embodiment 3 of this application;

[0066] Figure 17 is a second schematic diagram of the connection between the crankshaft and the lower bearing in Embodiment 3 of this application;

[0067] Figure 18 is a structural schematic diagram of the crankshaft of Embodiment 3 of this application;

[0068] Figure 19 is a schematic cross-sectional view along the BB direction shown in Figure 2;

[0069] Figure 20 is one of the structural schematic diagrams of the lower bearing in Embodiment 3 of this application;

[0070] Figure 21 is a second schematic diagram of the structure of the lower bearing in Embodiment 3 of this application;

[0071] Figure 22 is a schematic cross-sectional view along the CC direction shown in Figure 21;

[0072] Figure 23 is a simulation curve of the wear amount of the short shaft and the lower bearing versus S / d in Embodiment 3 of this application;

[0073] Figure 24 is a simulation curve of the oil film thickness of the short shaft versus θ / L in Embodiment 3 of this application.

[0074] Explanation of reference numerals in the attached drawings: 10. Compressor housing; 20. Stator; 21. Joint; 22. Recess; 23. Coil slot; 24. First refrigerant passage; 30. Rotor; 31. Second refrigerant passage; 40. Crankshaft; 41. Long shaft; 42. Eccentric shaft; 43. Short shaft; 50. Pump body structure; 501. Upper silencer chamber; 502. Lower silencer chamber; 503. Refrigerant passage; 504. Bolt passage; 51. Upper silencer cover; 511. Exhaust port; 52. Upper bearing; 521. Upper exhaust valve 522. Upper through hole; 53. Cylinder; 531. Cylinder body; 532. Flange; 533. Compression chamber; 534. Upper exhaust notch; 535. Lower exhaust notch; 536. Oil return passage; 537. Intake passage; 538. Suction hole; 54. Lower bearing; 541. Lower exhaust through hole; 542. Lower exhaust valve seat; 543. Lower through hole; 544. Rotating oil groove; 544A. Upper end line; 544B. Lower end line; 55. Lower muffler cover; 60. Electric component. Detailed Implementation

[0075] Example 1:

[0076] In response to the defects existing in compressors using single-cylinder pump bodies, the applicant analyzed and studied the structure and working principle of compressors using single-cylinder pump bodies and found that: the existing single-cylinder pump body adopts the method of upper and lower exhaust. When the refrigerant is discharged from the lower exhaust port of the cylinder, it needs to pass through the lower bearing into the lower muffler cover, and then pass through the channel that runs through the lower bearing, cylinder and upper bearing into the upper muffler cover, and finally be discharged from the pump body. However, the lower exhaust port of the single-cylinder pump body is located below the oil level of the compressor housing. When exhausting downwards, a narrow passage can lead to greater resistance for the refrigerant, resulting in higher electrical input. Conversely, a large passage can cause refrigerant leakage due to the reduced distance between the passage and the cylinder interior. Furthermore, the heat from the high-temperature refrigerant in the passage is transferred to the cylinder, increasing the heat of the refrigerant inside. The large passage also causes a sudden drop in the compressed gas pressure, leading to some high-pressure gas flowing back into the low-pressure chamber, disrupting the pressure balance within the cylinder and causing the refrigerant to circulate under non-design conditions, increasing ineffective heat exchange and thus increasing heat loss. Additionally, the reduced distance between the passage and the cylinder exterior can lead to lubricant seepage, increasing the pump's oil discharge and reducing compressor efficiency. Moreover, the compressor pump body is typically connected to the compressor housing via bearings, causing the pump's natural frequency to resonate with other components, resulting in increased noise.

[0077] In response to the above findings, this application provides a compressor and HVAC equipment that, by setting up several refrigerant channels connecting the upper and lower silencers, effectively reduces the electrical input and heat exchange losses during pump discharge, thereby improving the energy efficiency of the refrigerant compressor and thus increasing its operating efficiency. Furthermore, the compressor of this application can also reduce compressor noise. The following are some specific embodiments of this application:

[0078] Referring to Figures 1 to 7, the compressor of this embodiment includes a compressor housing 10, a stator 20, a rotor 30, a crankshaft 40, a pump body structure 50, and an electric actuator 60. The compressor housing 10 is a hollow shell. The stator 20, rotor 30, crankshaft 40, pump body structure 50, and electric actuator 60 are disposed within the compressor housing 10. The rotor 30 is coaxially disposed within the stator 20 and rotates around its axis. The crankshaft 40 is connected to the rotor 30 to drive the crankshaft 40 to rotate eccentrically. The pump body structure 50 is disposed on the inner peripheral wall of the compressor housing 10 and is located below the stator 20 and rotor 30. The crankshaft 40 extends into the interior of the pump body structure 50. The electric actuator 60 is drivenly connected to the crankshaft 40.

[0079] The pump body structure 50 is coaxially disposed inside the compressor housing 10, and includes an upper silencer cover 51, an upper bearing 52, a cylinder 53, a lower bearing 54, and a lower silencer cover 55 arranged sequentially along the axial direction of the rotor 30. The upper silencer cover 51 has an air outlet 511, and an upper silencer cavity 501 is formed between the upper silencer cover 51 and the upper bearing 52. The outer peripheral wall of the cylinder 53 is connected to the inner peripheral wall of the compressor housing 10. The lower silencer cover 55 and the lower bearing 54 form a lower silencer cavity 502. The lower bearing 54 has a lower exhaust port 541 that connects the interior of the cylinder 53 and the lower muffler cavity 502. The upper bearing 52, the sidewall of the cylinder 53, and the lower bearing 54 have several refrigerant channels 503 that connect the upper muffler cavity 501 and the lower muffler cavity 502, extending axially through them. The cylinder 53 includes a cylinder body 531 and a flange portion 532 fitted onto the outer periphery of the cylinder body 531. The outer periphery of the flange portion 532 is connected to the inner periphery of the compressor housing 10. Alternatively, the cylinder 53 can be directly welded to the inner periphery of the compressor housing 10 for direct fixation.

[0080] In this embodiment, the inner diameter of the compressor housing 10 is D, and the discharge capacity of the pump structure 50 is V. The discharge capacity V of the pump structure 50 and the inner diameter D of the compressor housing 10 satisfy the relationship: 4V / πD.2 ≥1.2mm, where π is pi; furthermore, the inner diameter of the lower exhaust port 541 is L, the number of refrigerant channels 503 is n, and the inner diameter of each refrigerant channel 503 is d. The inner diameter d of the refrigerant channel 503 satisfies the following relationship with n and the number of refrigerant channels 503: 2≤n*d 2 / L 2 ≤4.

[0081] Furthermore, the upper bearing 52 and the lower bearing 54 are respectively disposed on the upper and lower end faces of the cylinder body 531, and the refrigerant channel 503 sequentially passes through the upper bearing 52, the cylinder body 531 and the lower bearing 54; the cylinder body 531 is provided with a compression chamber 533 inside, and the refrigerant channel 503 is separated from the compression chamber 533. The radial width of the cylinder body 531 is t, and the radial width t of the cylinder body 531 and the inner diameter d of the refrigerant channel 503 satisfy the relationship: 2≤t / d≤2.5.

[0082] Furthermore, in this embodiment, the upper end face of the cylinder body 531 is provided with an upper exhaust notch 534 communicating with the compression chamber 533, and the upper bearing 52 is provided with an upper exhaust valve seat 521 communicating with the upper exhaust notch 534 and the upper muffler chamber 501; the lower end face of the cylinder body 531 is provided with a lower exhaust notch 535 communicating with the compression chamber 533, and the lower bearing 54 is provided with a lower exhaust valve seat 542 communicating with the lower exhaust notch 535, and the lower exhaust through hole 541 is communicating with the lower exhaust valve seat 542.

[0083] Figure 8 shows a simulation curve of the heat exchange loss of the refrigerant compressor in this embodiment. As can be seen from Figure 8, when n*d 2 / L 2 When n*d < 2, the refrigerant discharge area is too small, leading to worsened refrigerant discharge resistance and a higher power input level; when n*d 2 / L 2 When the temperature exceeds 4, the excessively large refrigerant exhaust area leads to an increase in the heat exchange of the high-temperature, high-pressure refrigerant, resulting in increased heat exchange losses and a rise in electrical input. Therefore, the relationship between the inner diameter L of the lower exhaust port 541 and the number n and inner diameter d of the refrigerant channels 503 is designed to be 2 ≤ n * d. 2 / L 2 When the value is ≤4, the heat exchange loss and power input of the compressor can be reduced, effectively improving the energy efficiency of the compressor.

[0084] As shown in Figure 9, which is a simulation diagram of the energy efficiency curve of the refrigerant compressor in this embodiment, it can be seen from Figure 9 that when t / d < 2, the wall thickness of the cylinder body 531 is too thin, and the refrigerant leakage in the refrigerant channel 503 worsens, resulting in a decrease in the compressor's energy efficiency. When t / d > 2.5, the inner diameter of the refrigerant channel 503 is too small, and with the refrigerant flow rate remaining constant, the friction loss along the refrigerant channel 503 increases, leading to a decrease in the compressor's energy efficiency. Therefore, the relationship between the inner diameter d of the refrigerant channel 503 and the radial width t of the cylinder body 531 is designed to be 2 ≤ t / d ≤ 2.5, which can effectively reduce the risk of refrigerant leakage while ensuring that the compressor's energy efficiency remains at a high level.

[0085] Therefore, according to the refrigerant compressor of this embodiment, during operation, at least a portion of the refrigerant flows from the lower exhaust port 535 of the compression chamber 533 through the lower exhaust valve seat 542 to the lower exhaust through-hole 541, then flows into the lower silencer chamber 502, and finally flows into the upper silencer chamber 501 through the refrigerant channel 503. In this process, the relationship between the inner diameter L of the lower exhaust through-hole 541 of the pump body structure 50 and the number n and inner diameter d of the refrigerant channels 503 is designed to be 2 ≤ n * d. 2 / L 2 The refrigerant discharged from the lower exhaust port 541 has sufficient space to smoothly drain into the upper silencer chamber 501 after entering the lower silencer chamber 502. This effectively improves the exhaust resistance of the pump structure, reduces the heat exchange loss of the compressor, and relatively reduces the required power input, thereby effectively improving the compressor's energy efficiency. Furthermore, according to this embodiment, the refrigerant compressor is designed with a relationship between the inner diameter d of the refrigerant channel 503 and the radial width t of the cylinder body 531 of 2≤t / d≤2.5. This ensures a certain sealing distance between the refrigerant channel 503 and both the inner and outer sides of the cylinder body 531. This effectively reduces the risk of refrigerant leakage in the refrigerant channel 503 while ensuring sufficient space for the refrigerant to smoothly drain into the upper silencer chamber 501, thereby effectively improving the compressor's efficiency.

[0086] The crankshaft 40 is sequentially connected to the upper muffler cover 51, the upper bearing 52, the cylinder body 531, the lower bearing 54, and the lower muffler cover 55, with the end of the crankshaft 40 located in the compression chamber 533.

[0087] In some embodiments, the diameter of the upper bearing 52 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the upper bearing 52 is smaller than the diameter of the flange portion 532; the diameter of the lower bearing 54 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the lower bearing 54 is smaller than the diameter of the flange portion 532. It can be understood that in these embodiments, the cylinder 53 is connected and fixed to the inner circumference of the compressor housing 10 via the outer circumference of the flange portion 532, while the upper bearing 52 and lower bearing 54 respectively cover the upper and lower end faces of the cylinder body 531. Due to the connection between the cylinder and the housing, the natural frequency of the pump structure is improved, resulting in noise reduction.

[0088] It can be understood that, in this embodiment, the pump body structure is a single-cylinder structure, and is fixedly connected to the compressor housing 10 through the flange 532 on the outer periphery of the cylinder 53; it uses a dual exhaust method of upper and lower exhaust for exhaust.

[0089] In some embodiments, a plurality of refrigerant channels 503 are spaced apart along the circumferential direction of the cylinder body 531 and projected axially along the rotor 30. Each refrigerant channel 503 has a bolt channel 504 on both sides. The bolt channel 504 sequentially passes through the upper muffler cover 51, the upper bearing 52, the cylinder body 531, the lower bearing 54, and the lower muffler cover 55. It can be understood that in these embodiments, the inner diameter of the bolt channel 504 is smaller than the inner diameter of the refrigerant channel 503. The entire pump body structure can be locked and fixed by passing screws through the bolt channel 504 and then using nuts, or by using rivets through the bolt channel 504.

[0090] In some embodiments, the flange portion 532 has an annular structure, and a plurality of oil return channels 536 are provided through the flange portion 532 in the axial direction. The plurality of oil return channels 536 are distributed at intervals along the circumference of the flange portion 532. It can be understood that, in the embodiment of the present invention, the cylinder 53, by providing the oil return channels 536 on the flange portion 532, facilitates the lubricating oil to fall back to the bottom of the pump body structure 50, thereby ensuring that the oil level inside the compressor housing 10 is at a certain height.

[0091] Furthermore, in some embodiments of this application, the axial height of the cylinder 53 along the compressor housing 10 is H, and the axial height H of the cylinder 53 along the compressor housing 10 satisfies the relationship between the inner diameter D of the compressor housing 10 and D: D / H < 4.5.

[0092] The following describes several specific embodiments of the compressor in this embodiment in detail with reference to Figures 1 to 8. It is worth understanding that the following specific embodiments are merely illustrative and should not be construed as limiting this application.

[0093] In some specific embodiments of this example, the compressor includes the compressor housing 10 and the pump body structure 50, and the inner diameter D of the compressor housing 10 and the discharge capacity V of the pump body structure 50 satisfy the relationship: 4V / πD 2 = 1.2mm; the pump body structure 50 is coaxially arranged inside the compressor housing 10; the inner diameter L of the lower exhaust port 541, the number n of the refrigerant channels 503, and the inner diameter d of each refrigerant channel 503 satisfy the following relationship: n*d 2 / L 2 =2.

[0094] Furthermore, the radial width t of the cylinder body 531 and the inner diameter d of each refrigerant channel 503 satisfy the relationship: t / d = 2.

[0095] The diameter of the upper bearing 52 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the upper bearing 52 is smaller than the diameter of the flange portion 532; the diameter of the lower bearing 54 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the lower bearing 54 is smaller than the diameter of the flange portion 532. Furthermore, the flange portion 532 has an annular structure, and a plurality of oil return channels 536 are provided through the flange portion 532 along the axial direction, with the plurality of oil return channels 536 spaced apart along the circumference of the flange portion 532.

[0096] Several refrigerant channels 503 are distributed at intervals along the circumference of the cylinder body 531. Each refrigerant channel 503 has a bolt channel 504 on both sides. The bolt channel 504 passes through the upper muffler cover 51, the upper bearing 52, the cylinder body 531, the lower bearing 54, and the lower muffler cover 55 in sequence.

[0097] In some other specific embodiments of this example, the inner diameter D of the compressor housing and the discharge capacity V of the pump structure 50 satisfy the following relationship: 4V / πD 2 = 1.2mm; the pump body structure 10 is coaxially arranged inside the compressor housing; the inner diameter L of the lower exhaust port 541, the number n of the refrigerant channels 503, and the inner diameter d of each refrigerant channel 503 satisfy the following relationship: n*d 2 / L 2 =3.

[0098] Furthermore, the radial width t of the cylinder body 531 and the inner diameter d of each refrigerant channel 503 satisfy the relationship: t / d = 2.3.

[0099] The diameter of the upper bearing 52 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the upper bearing 52 is smaller than the diameter of the flange portion 532; the diameter of the lower bearing 54 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the lower bearing 54 is smaller than the diameter of the flange portion 532. Furthermore, the flange portion 532 has an annular structure, and a plurality of oil return channels 536 are provided through the flange portion 532 along the axial direction, with the plurality of oil return channels 536 spaced apart along the circumference of the flange portion 532.

[0100] Several refrigerant channels 503 are distributed at intervals along the circumference of the cylinder body 531. Each refrigerant channel 503 has a bolt channel 504 on both sides. The bolt channel 504 passes through the upper muffler cover 51, the upper bearing 52, the cylinder body 531, the lower bearing 54, and the lower muffler cover 55 in sequence.

[0101] In some other specific embodiments of this example, the inner diameter D of the compressor housing and the discharge capacity V of the pump structure 50 satisfy the following relationship: 4V / πD 2 = 1.3mm; the pump body structure is coaxially arranged inside the compressor housing; the inner diameter L of the lower exhaust port 541, the number n of the refrigerant channels 503, and the inner diameter d of each refrigerant channel 503 satisfy the following relationship: n*d 2 / L 2 =4.

[0102] Furthermore, the radial width t of the cylinder body 531 and the inner diameter d of each refrigerant channel 503 satisfy the relationship: t / d = 2.5.

[0103] The diameter of the upper bearing 52 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the upper bearing 52 is smaller than the diameter of the flange portion 532; the diameter of the lower bearing 54 is greater than or equal to the diameter of the cylinder body 531, and the diameter of the lower bearing 54 is smaller than the diameter of the flange portion 532. Furthermore, the flange portion 532 has an annular structure, and a plurality of oil return channels 536 are provided through the flange portion 532 along the axial direction, with the plurality of oil return channels 536 spaced apart along the circumference of the flange portion 532.

[0104] Furthermore, in this embodiment, several refrigerant channels 503 are spaced apart along the circumference of the cylinder body 531, and bolt channels 504 are provided on both sides of each refrigerant channel 503. The bolt channels 504 pass through the upper muffler cover 51, the upper bearing 52, the cylinder body 531, the lower bearing 54, and the lower muffler cover 55 in sequence.

[0105] It is understood that the above specific embodiments are merely illustrative and should not be construed as limiting this application.

[0106] Furthermore, in this embodiment, the compressor housing 10 is a sealed container for storing refrigeration oil. The electric component 60 is housed inside the compressor housing 10. The electric component 60 is used to connect to an external power source to supply power to the rotor, stator, etc., driving the pump body structure 50 to compress the refrigerant. The electric component 60 may include an electrically connected motor, terminals, cables, capacitors, a control circuit board, and a temperature sensor. Since the electric component 60 is a conventional design in the prior art, it will not be described in detail here.

[0107] The refrigerant compressed by the pump body structure is at least a natural refrigerant, an HFC refrigerant, or an HFO refrigerant. Furthermore, the refrigeration oil is at least one of POE oil and PVE oil, or a mixture thereof.

[0108] In some embodiments, the natural refrigerant is at least one of R290 and CO2, or a mixture thereof; the HFC refrigerant is at least one of R32, R410A, R134a, R404A, and R407C, or a mixture thereof; and the HFO refrigerant is at least one of R454B, R454C, R513A, and R1234yf, or a mixture thereof.

[0109] In addition, a heating and ventilation device is provided, including the compressor of Embodiment 1. The heating and ventilation device according to embodiments of the present invention can effectively reduce the electrical input and heat exchange losses during pump structure exhaust, thereby improving the energy efficiency of the compressor.

[0110] Example 2:

[0111] During the analysis and research of the structure and working principle of the compressor using a single-cylinder pump body, the applicant also discovered that, in addition to improving the setting of the refrigerant exhaust channel, heat exchange efficiency can be improved from other aspects. This is because, during the compression process of the refrigerant in the pump body structure 50, the refrigeration oil dissolves in the refrigerant. Then, the refrigerant mixed with the refrigeration oil passes sequentially through the refrigerant channel 503, the space above the stator 20, and finally exits the compressor from the exhaust port at the top of the compressor housing 10. In this process, the refrigeration oil gradually separates from the gaseous refrigerant under the influence of gravity and velocity, and returns to the lower end of the compressor housing 10 through the gap between the stator 20 and the compressor housing 10.

[0112] The heat exchange efficiency of the above process is affected by the compressor's outer diameter because: for compressors with small outer diameters, the internal space is limited. After the refrigerant and refrigeration oil separate in the space above the pump body structure 50, the channel area for the oil to descend is insufficient. This easily leads to a large amount of refrigerant oil floating above the stator 20 or in the area between the pump body structure 50 and the stator 20. As a result, less refrigerant oil falls back to the bottom of the compressor. A low oil level can easily lead to insufficient lubrication of the pump body structure 50, thereby reducing the compressor's service life. In addition, because the refrigerant oil floats at the top of the compressor, the refrigerant discharge process will mix with this floating refrigerant oil again, resulting in more refrigerant oil mixed in with the refrigerant discharged from the compressor, ultimately affecting the heat exchange efficiency of the air conditioning system. Furthermore, as the space requirements for existing compressors become smaller and smaller, small-diameter, large-displacement compressors become increasingly common, the heat exchange efficiency problem caused by reducing the compressor's outer diameter becomes increasingly prominent.

[0113] As can be seen from the above findings, in addition to the refrigerant discharge passage configuration, the amount of refrigeration oil discharged also affects the compressor's energy efficiency. Therefore, in this embodiment, the applicant also provides a compressor that, by improving the structure of the stator and rotor, ensures that the total area S of the stator, rotor, and compressor housing for refrigerant passage satisfies a certain proportional relationship with the discharge volume V of the pump structure. This achieves good iron loss performance while effectively reducing the amount of refrigeration oil discharged from the compressor, thereby reducing the amount of refrigeration oil discharged and maintaining the oil level in the pump structure at a normal level, thus effectively extending the service life of the pump structure and the compressor. The specific implementation of the compressor in this embodiment is as follows:

[0114] Please refer to Figures 10 to 13; the compressor of this embodiment includes a compressor housing 10, a stator 20, a rotor 30, and a pump body structure 50 as described in Embodiment 1; the stator 20 has a connecting portion 21 and a recessed portion 22 on its outer peripheral side, the connecting portion 21 is connected to the inner peripheral wall of the compressor housing 10, and the recessed portion 22 is clearance-fitted with the inner peripheral wall of the compressor housing 10; the rotor 30 is coaxially disposed inside the stator 20, and the rotor 30 is clearance-fitted with the stator 20; the pump body structure 50 is disposed on the inner peripheral wall of the compressor housing 10, and the pump body structure 50 is located below the stator 20 and the rotor 30, and the rotor 30 drives the pump body structure 50.

[0115] The area of ​​the gap between the recessed portion 22 and the compressor housing 10 is S1. The stator 20 is provided with a plurality of coil slots 23. Each coil slot 23 and the coil located in the coil slot 23 form a first refrigerant channel 24. The area of ​​the first refrigerant channel 24 is S2. The area of ​​the gap between the stator 20 and the rotor 30 is S3. The rotor 30 is provided with a second refrigerant channel 31. The area of ​​the second refrigerant channel 31 is S4. The total area of ​​the compressor housing 10 for refrigerant to pass through in the axial direction is S. S satisfies the relationship: S=S1+S2+S3+S4. The discharge volume V of the pump body structure 50 and the total area S satisfy the relationship: 10mm≤V / S≤15mm.

[0116] Specifically, in this embodiment, the inner diameter D of the compressor housing 10 and the discharge volume V of the pump structure 50 satisfy the relationship: 4V / πD 2 ≥1.2mm; where π is the ratio of π to pi. Furthermore, the coil slot 23 and the coil in the slot of the stator 20 in this embodiment can be understood, based on existing technology, as follows: the stator 20 includes an annular stator yoke and a plurality of stator teeth extending radially inward on the inner circumferential side of the stator yoke; the coil slot 23 is formed between two adjacent stator teeth; and a wire assembly is wound in the coil slot 23 to form the coil in the slot.

[0117] As shown in Figure 14, this figure illustrates the relationship between the oil quantity in the compressor housing 10 and the iron loss in the stator 20 in this embodiment. Figure 14 shows that the ratio V / S is directly proportional to the oil quantity and inversely proportional to the iron loss in the stator 20. When V / S ≤ 15 mm, the oil quantity curve is relatively stable and at a low level; however, when V / S > 15 mm, the oil quantity curve rises rapidly and reaches a high level. Furthermore, when V / S ≤ 10 mm, although the iron loss curve in the stator 20 shows a downward trend, the iron loss is significantly deteriorating. When V / S > 15 mm, the iron loss curve in the stator 20 is relatively stable and at a low level. Therefore, considering the combined effects of the oil quantity in the compressor housing 10 and the iron loss in the stator 20, when the V / S ratio is limited to 10 mm ≤ V / S ≤ 15 mm, the compressor in this embodiment can effectively reduce the amount of refrigerant oil discharged while maintaining a low iron loss in the stator 20, thereby improving the compressor's oil discharge problem and enhancing its performance.

[0118] Therefore, according to this embodiment, by improving the structure of the stator 20 and the rotor 30, and limiting the ratio between the total area S of the stator 20 and the compressor housing 10 for refrigerant to pass through in the axial direction to the discharge volume V of the pump structure 50 to 8mm≤V / S≤15mm, the iron loss of the compressor can be maintained on a good basis while effectively reducing the discharge of refrigerant oil from the compressor. This reduces the amount of refrigerant oil discharged by the compressor, and the oil level of the pump structure can be maintained at a normal level, effectively extending the service life of the pump structure and the compressor. In addition, by providing the recessed portion 22 on the outer periphery of the stator 20, the contact area between the stator 20 and the compressor housing 10 is reduced, which can avoid the deformation caused by the stator 20 being heat-fitted to the compressor housing 10 through the joint portion 21.

[0119] In addition, in this embodiment, the oil return channel 536 extends through the pump body structure 50 along the axial direction. The area of ​​the oil return channel 536 is S5. The relationship between the area S5 of the oil return channel 536 and the discharge volume V of the pump body structure 50 is: 8mm≤V / S5≤12mm. The relationship between the area S5 of the oil return channel 536 and the total area S of the compressor housing 10 for refrigerant to pass through in the axial direction is: 0.7≤S / S5≤0.9. This structural design ensures that the ratio between the area S5 of the oil return channel 536 on the pump body structure 50 and the discharge volume V of the pump body structure 50 is limited to 8mm ≤ V / S5 ≤ 12mm, guaranteeing smooth oil return in the pump body structure. Furthermore, the ratio between the area S5 of the oil return channel 536 on the pump body structure and the total axial area S of the compressor housing 10 for refrigerant passage is limited to 0.7 ≤ S / S5 ≤ 0.9, effectively maintaining the refrigeration oil level in a favorable condition and keeping the oil level in the pump body structure at a normal level, thus effectively extending the service life of the pump body structure and the compressor.

[0120] As shown in Figure 15, this figure illustrates the relationship between the oil level and V / S5 of the compressor in this embodiment. Figure 15 shows that V / S5 and oil level are inversely proportional. When V / S5 is limited to ≤12mm, the oil level is relatively high, and the curve shows little change. However, when V / S5 > 12mm, the oil level drops rapidly and deteriorates. Furthermore, due to the structural limitations of the pump body structure 50, increasing processing difficulty occurs when V / S5 < 8mm. Therefore, when V / S5 is within the range of 8mm ≤ V / S5 ≤ 12mm, the refrigeration oil level can be effectively maintained at a good level, thus keeping the oil level in the compressor housing 10 at a high position.

[0121] In some other embodiments of this example, the pump body structure 50 is placed inside the cylinder 53 and has a compression chamber 533 with openings at both ends. The outer side wall of the cylinder 53 is recessed in the radial direction to form an air intake channel 537 that connects to the compression chamber 533. The upper bearing 52 and the lower bearing 54 are respectively disposed above and below the compression chamber 533. The flange 532 is fitted and connected to the inner peripheral wall of the compressor housing 10. Several arc-shaped channels are distributed along the circumferential direction on the cylinder 53, penetrating both ends of the cylinder 53. The several arc-shaped channels together form the oil return channel 536.

[0122] It is worth noting that in other specific embodiments of this example, the pump body structure 50 may also have an oil return channel on the upper bearing 52 through which the refrigerant oil can fall back. In these embodiments, the outer diameter of the upper bearing 52 is designed to be larger than the outer diameter of the cylinder 53, and the pump body structure 50 is connected to the compressor housing 10 through the outer periphery of the upper bearing 52. That is to say, in these embodiments, the oil return channel can be located on either the upper bearing 52 or the cylinder 53, depending on the specific requirements.

[0123] Furthermore, in some embodiments, a plurality of joint portions 21 are evenly distributed on the outer periphery of the stator 20, and a recessed portion 22 is provided between two adjacent joint portions 21. The recessed portion 22 is formed by recessing inward from the outer periphery of the stator 20, and the arc length of the recessed portion 22 in the circumferential direction is smaller than the arc length of the joint portion 21 in the circumferential direction. It can be understood that, in these embodiments, by providing the recessed portion 22 on the outer periphery of the stator 20, the contact surface between the stator 20 and the compressor housing 10 is reduced, which can avoid the defective phenomenon caused by the stator 20 being heat-fitted to the compressor housing 10 through the joint portion 21.

[0124] The following describes several specific embodiments of the compressor of this embodiment in detail with reference to Figures 10 to 13. It is worth understanding that the following specific embodiments are merely illustrative and should not be construed as limiting the present application.

[0125] As some specific embodiments of the compressor in this example, the gap area S1 formed between the recess 22 and the compressor housing 10, the area S2 of the first refrigerant passage 24, the gap area S3 formed between the stator 20 and the rotor 30, the area S4 of the second refrigerant passage 31, and the total area S of the interior of the compressor housing 10 for refrigerant to pass through in the axial direction satisfy the following relationship: S = S1 + S2 + S3 + S4; the discharge volume V of the pump body structure 50 and the total area S satisfy the following relationship: V / S = 10mm.

[0126] Furthermore, the inner diameter D of the compressor housing 10 and the discharge capacity V of the pump structure 50 satisfy the following relationship: 4V / πD 2 =1.2mm. The area S5 of the oil return channel 536 and the exhaust volume V of the pump body structure 50 satisfy the following relationship: V / S5 = 8mm; the area S5 of the oil return channel 536 and the total area S satisfy the following relationship: S / S5 = 0.8.

[0127] In these specific embodiments, the arc length of the recessed portion 22 in the circumferential direction is smaller than the arc length of the connecting portion 21 in the circumferential direction.

[0128] In other specific embodiments of the compressor in this example, the gap area S1 formed between the recess 22 and the compressor housing 10, the area S2 of the first refrigerant passage 24, the gap area S3 formed between the stator 20 and the rotor 30, the area S4 of the second refrigerant passage 31, and the total area S of the compressor housing 10 for refrigerant to pass through in the axial direction satisfy the following relationship: S = S1 + S2 + S3 + S4; the discharge volume V of the pump body structure 50 satisfies the following relationship with the total area S: V / S = 12 mm.

[0129] Furthermore, the inner diameter D of the compressor housing 10 and the discharge capacity V of the pump structure 50 satisfy the following relationship: 4V / πD 2 =1.2mm. In addition, the area S5 of the oil return channel 536 and the exhaust volume V of the pump body structure 50 satisfy the following relationship: V / S5 = 10mm; the area S5 of the oil return channel 536 and the total area S satisfy the following relationship: S / S5 = 0.9.

[0130] In these specific embodiments, the arc length of the recessed portion 22 in the circumferential direction is smaller than the arc length of the connecting portion 21 in the circumferential direction.

[0131] In other specific embodiments of the compressor in this example, the gap area S1 formed between the recess 22 and the compressor housing 10, the area S2 of the first refrigerant passage 24, the gap area S3 formed between the stator 20 and the rotor 30, the area S4 of the second refrigerant passage 31, and the total area S of the compressor housing 10 for refrigerant to pass through in the axial direction satisfy the following relationship: S = S1 + S2 + S3 + S4; the discharge volume V of the pump body structure 50 satisfies the following relationship with the total area S: V / S = 15mm.

[0132] Furthermore, the inner diameter D of the compressor housing 10 and the discharge capacity V of the pump structure 50 satisfy the following relationship: 4V / πD 2 =1.3mm. In addition, the area S5 of the oil return channel 536 and the exhaust volume V of the pump body structure 50 satisfy the following relationship: V / S5 = 12mm; the area S5 of the oil return channel 536 and the total area S satisfy the following relationship: S / S5 = 0.7.

[0133] In these specific embodiments, the arc length of the recessed portion 22 in the circumferential direction is smaller than the arc length of the connecting portion 21 in the circumferential direction.

[0134] Furthermore, similar to Embodiment 1, the compressor housing 10 in this embodiment can be a sealed container for storing refrigeration oil, and the pump structure 50 is used to compress the refrigerant, which will not be described again here.

[0135] A heating and ventilation (HVAC) device is also provided, including the compressor of Embodiment 2 described above. The HVAC device according to this embodiment enables sufficient separation of refrigerant and refrigeration oil, effectively improving the oil discharge problem of the compressor, thereby increasing the compressor's service life and operating efficiency.

[0136] Example 3:

[0137] During the analysis and research of the structure and working principle of a compressor with a single-cylinder pump body and a small outer diameter, the applicant also discovered that, in addition to the need to improve heat exchange efficiency, the compressor is prone to sintering between the short shaft and the lower bearing of the crankshaft, reducing its reliability. This is because, for a small-diameter compressor, during operation, the high-temperature, high-pressure refrigerant exerts a reverse force on the crankshaft, especially on the short shaft, requiring it to bear a certain load. Furthermore, due to the limited space in a small-diameter compressor, to achieve a large displacement, the length and eccentricity of the eccentric shaft are generally increased to improve the compressor's displacement. However, the load on the eccentric shaft also increases with the increase in length and eccentricity, transferring some of the load to the short shaft, leading to increased load on the short shaft and further accelerating its wear.

[0138] In response to the above findings, in this embodiment, the applicant also provides a compressor that, through structural improvements to the crankshaft and lower bearing, allows the lubricating oil to more smoothly lubricate the short shaft and lower bearing, effectively reducing the load on the short shaft and the wear between the short shaft and the lower bearing, and preventing sintering between the short shaft and the lower bearing. The specific implementation of the compressor in this embodiment is as follows:

[0139] Please refer to Figures 16 to 22. This embodiment provides a compressor, including a crankshaft 40 and a pump body structure 50. The pump body structure 50 includes an upper bearing 52, a cylinder 53, and a lower bearing 54. The cylinder 53 has an axially extending compression chamber 533. The upper bearing 52 and the lower bearing 54 are respectively disposed on the upper and lower end faces of the cylinder 53. The upper bearing 52 has an upper through hole 522 extending through its axis, communicating with the compression chamber 533. The lower bearing 54 has a lower through hole 543 extending through its axis, communicating with the compression chamber 533. The crankshaft 40 includes a long shaft 41, an eccentric shaft 42, and a short shaft 43 connected axially in sequence. The long shaft 41 passes through the upper through hole 522, the eccentric shaft 42 is disposed in the compression chamber 533, and the short shaft 43 is disposed in the lower through hole 543. In the lower through hole 543; the shortest distance from the axis of the eccentric shaft 42 to the axis of the long shaft 41 is E, the diameter of the short shaft 43 is d1, and the shortest distance E from the axis of the eccentric shaft 42 to the axis of the long shaft 41 and the diameter d1 of the short shaft 43 satisfy the relationship: E / d1≤0.35; the axial length of the eccentric shaft 42 is H1, and the axial length of the short shaft 43 is h; the axial length H1 of the eccentric shaft 42 and the axial length h of the short shaft 43 satisfy the relationship: H1 / h≤1.2; a rotating oil groove 544 is recessed on the inner wall of the lower through hole 543, and the two ends of the rotating oil groove 544 respectively penetrate the two ends of the lower through hole 543. In this embodiment, the rotating oil groove 544 penetrates the lower bearing 54 in a direction inclined relative to the axial direction of the crankshaft 40. The radial cross-sectional area of ​​the rotating oil groove 544 is S6, and the radial cross-sectional area S6 of the rotating oil groove 544 and the diameter d1 of the short shaft 43 satisfy the following relationship: 0.05mm≤S6 / d1≤0.1mm.

[0140] Please refer to Figure 23, which is a simulation curve of the wear amount of the short shaft 43 and the lower bearing 54 in this embodiment versus S6 / d1. As can be seen from Figure 23, when S6 / d1 < 0.05 mm, the flow area of ​​the rotating oil groove 544 is too small, making it difficult for lubricating oil to reach the inner wall of the lower through hole 543 of the lower bearing 54. This results in a large wear amount between the short shaft 43 and the lower bearing 54, making sintering between them more likely. When S6 / d1 > 0.1 mm, the flow area of ​​the rotating oil groove 544 is too large, reducing the contact area between the inner wall of the lower through hole 543 of the lower bearing 54 and the short shaft 43. This increases the pressure on the lower bearing 54 per unit area, and the wear amount of the short shaft 43 and the lower bearing 54 also shows a corresponding upward trend. Therefore, when the radial cross-sectional area S6 of the rotating oil groove 544 and the diameter d1 of the short shaft 43 satisfy the relationship 0.05mm≤S6 / d1≤0.1mm, the lubricating oil can flow more smoothly along the rotating oil groove 544 to the inner wall of the lower through hole 543 of the lower bearing 54, the eccentric shaft 42 and other components, and is conducive to the formation of an oil film between the short shaft 43 and the lower bearing 54, effectively reducing the wear between the short shaft 43 and the lower bearing 54.

[0141] Further, as shown in Figure 21, in this embodiment, the rotating oil groove 544 is recessed on the inner side of the lower bearing 54. In the axial direction of the short shaft 43, it forms the upper end line 544A and the lower end line 544B of the rotating oil groove 544 with the lower bearing 54. The upper end line 544A is close to one end of the upper bearing 52, and the lower end line 544B is located away from the upper bearing 52. The height L1 of the rotating oil groove 544 is the distance between the upper end line 544A and the lower end line 544B in the axial direction of the short shaft 43. When the rotating oil groove 544 penetrates the lower bearing 54, the height L1 of the rotating oil groove 544 is equal to the axial length L of the lower through hole 543. Projecting along the short axis 43, both the upper end line 544A and the lower end line 544B are arcs. Connecting the center of the upper end line 544A to the center of the lower through hole 543, and the center of the lower end line 544B to the center of the lower through hole 543, respectively, yields a first connecting line l1 and a second connecting line l2. The included angle between the first connecting line l1 and the second connecting line l2 is the rotation angle θ of the rotating oil groove 544. The height L1 of the rotating oil groove 544 satisfies the relationship between the rotation angle θ and the height L1: 2° / mm ≤ θ / L1 ≤ 4° / mm.

[0142] Further, as shown by the arrow in Figure 19, the rotation direction of the short shaft 43 is defined as the direction in which the centerline of the intake hole 538 rotates to the centerline of the lower exhaust hole 541 at its maximum angle. As shown by the arrow in Figure 21, the rotation direction of the rotating oil groove 544 is defined as the direction in which the first connecting line l1 turns towards the second connecting line l2. The rotation direction of the rotating oil groove 544 is opposite to the rotation direction of the short shaft 43.

[0143] In this embodiment, referring to Figures 2 and 19, refrigerant is drawn from the reservoir into the cylinder 53 through the suction port 538. Projected along the axis of the cylinder 53, the center line l of the suction port 538 passes through the center O of the cylinder 53. Connecting the center A of the lower exhaust port 541 and the center O of the cylinder 53, a straight line OA is obtained. The rotation direction of the short axis 43 is the direction in which the center line l rotates to coincide with the straight line OA after the maximum rotation angle, i.e., the counterclockwise rotation direction.

[0144] Please refer to Figure 24, which is a simulation curve of the oil film thickness of the short shaft 43 versus θ / L1 in this embodiment. As can be seen from Figure 24, when θ / L1 < 2° / mm, the rotation angle of the rotating oil groove 544 is too small. The lubricating oil, under its own weight, has difficulty rotating with the short shaft 43, resulting in less lubricating oil at the upper end of the short shaft 43 and a correspondingly thinner oil film, leading to increased wear between the short shaft 43 and the lower bearing 54. When θ / L1 > 4° / mm, the rotation angle of the rotating oil groove 544 is too large, increasing the path length of the rotating oil groove 544 and the flow path of the lubricating oil. This makes it difficult for the lubricating oil to rise through the rotating oil groove 544 to the upper end of the short shaft 43, causing the oil film thickness of the short shaft 43 to decrease, and the wear between the short shaft 43 and the lower bearing 54 to increase accordingly. Therefore, when 2° / mm≤θ / L1≤4° / mm, the inclination of the rotating oil groove 544 can be maintained within a certain range, and the oil film thickness formed between the short shaft 43 and the lower through hole 543 can reach a relatively thick value, thereby effectively reducing the wear between the short shaft 43 and the lower bearing 54 and avoiding sintering between the short shaft 43 and the lower bearing 54.

[0145] Therefore, according to this embodiment, the compressor improves the structure of the eccentric shaft 42, the short shaft 43, and the lower bearing 54 of the crankshaft 40 so that the shortest distance E from the axis of the eccentric shaft 42 to the axis of the long shaft 41 satisfies the relationship E / d1≤0.35 with the diameter d1 of the short shaft 43. This effectively reduces the load on the short shaft 43 while ensuring the displacement. Furthermore, by providing the rotating oil groove 544 on the inner wall of the lower through hole 543 of the lower bearing 54, the radial direction of the rotating oil groove 544 is improved. The cross-sectional area S6 and the diameter d1 of the short shaft 43 satisfy the relationship 0.05mm≤S6 / d1≤0.1mm. This allows the lubricating oil to flow more smoothly along the rotating oil groove 544 to the inner wall of the lower through hole 543 of the lower bearing 54, the eccentric shaft 42, and other components. It also facilitates the formation of an oil film between the short shaft 43 and the lower bearing 54, effectively reducing wear between them and preventing sintering. This significantly improves the reliability of the compressor. Furthermore, according to the compressor of this embodiment, by ensuring that the rotation angle θ of the rotating oil groove 544 and the height L1 of the rotating oil groove 544 satisfy the relationship: 2° / mm≤θ / L1≤4° / mm, the inclination of the rotating oil groove 544 can be maintained within a certain range. This allows the oil film thickness formed between the short shaft 43 and the lower through hole 543 to reach a relatively thick value, thereby effectively reducing the wear between the short shaft 43 and the lower bearing 54, avoiding sintering between the short shaft 43 and the lower bearing 54, and effectively improving the reliability of the refrigerant compressor.

[0146] In this embodiment, the ratio between the shortest distance E from the axis of the eccentric shaft 42 to the axis of the major axis 41 and the diameter d1 of the minor axis 43 can be limited to: E / d1≤0.35, and the ratio between the axial length H1 of the eccentric shaft 42 and the axial length h of the minor axis 43 can be limited to: H1 / h≤1.2. This can prevent the minor axis 43 from bearing excessive load due to the excessive axial length H1 of the eccentric shaft 42.

[0147] In addition, similar to Embodiment 1, the compressor housing 10 in this embodiment can be a sealed container for storing refrigeration oil, and its interior can house an electric component 60 for driving the pump structure 50 to compress the refrigerant, which will not be described again here.

[0148] The following detailed description of some specific embodiments of the compressor of this application, with reference to Figures 16 to 22, is as follows. It is worth understanding that the specific embodiments below are merely illustrative and should not be construed as limiting the present application.

[0149] As one specific embodiment of the compressor in this example, it includes the crankshaft 40 and the pump body structure 50. The pump body structure 50 includes an upper muffler cover 51, an upper bearing 52, a cylinder 53, a lower bearing 54, and a lower muffler cover 55. The cylinder 53 has a compression chamber 533 extending through it in the axial direction. The upper bearing 52 and the lower bearing 54 are respectively disposed on the upper and lower end faces of the cylinder 53. The shortest distance E from the axis of the eccentric shaft 42 to the axis of the long shaft 41 and the diameter d1 of the short shaft 43 satisfy the relationship: E / d1 = 0.35; the axial length H1 of the eccentric shaft 42 and the axial length h of the short shaft 43 satisfy the relationship: H1 / h = 1.2; the radial cross-sectional area S6 of the rotating oil groove 544 and the diameter d1 of the short shaft 43 satisfy the relationship: S6 / d1 = 0.1 mm.

[0150] Furthermore, the rotation angle θ of the rotating oil groove 544 and the height L1 of the rotating oil groove 544 satisfy the relationship: θ / L1=4° / mm. The rotation direction of the rotating oil groove 544 is opposite to the rotation direction of the short shaft 43.

[0151] In other specific embodiments of the compressor in this example, the shortest distance E from the axis of the eccentric shaft 42 to the axis of the major shaft 41 satisfies the relationship d1 of the minor shaft 43: E / d1 = 0.30; the axial length H1 of the eccentric shaft 42 satisfies the relationship h of the axial length h of the minor shaft 43: H1 / h = 1.2; and the radial cross-sectional area S6 of the rotating oil groove 544 satisfies the relationship d1 of the minor shaft 43: S6 / d1 = 0.075 mm.

[0152] Furthermore, the rotation angle θ of the rotating oil groove 544 and the height L1 of the rotating oil groove 544 satisfy the relationship: θ / L1=3° / mm. The rotation direction of the rotating oil groove 544 is opposite to the rotation direction of the short shaft 43.

[0153] In other specific embodiments of the compressor in this example, the shortest distance E from the axis of the eccentric shaft 42 to the axis of the long shaft 41 and the diameter d1 of the short shaft 43 satisfy the following relationship: E / d1 = 0.35; the axial length H1 of the eccentric shaft 42 and the axial length h of the short shaft 43 satisfy the following relationship: H1 / h = 1.1; the radial cross-sectional area S of the rotating oil groove 544 and the diameter d1 of the short shaft 43 satisfy the following relationship: S6 / d1 = 0.05 mm.

[0154] Furthermore, the rotation angle θ of the rotating oil groove 544 and the height L1 of the rotating oil groove 544 satisfy the relationship: θ / L1=2° / mm. The rotation direction of the rotating oil groove 544 is opposite to the rotation direction of the short shaft 43.

[0155] Furthermore, this embodiment also provides a heating and ventilation device, including the compressor of embodiment three. According to the heating and ventilation device of this embodiment, by structurally improving the crankshaft and lower bearing, the lubricating oil can more smoothly lubricate the short shaft and lower bearing, effectively reducing the load on the short shaft and the wear between the short shaft and the lower bearing, and preventing sintering between the short shaft and the lower bearing.

[0156] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "left," "right," "top," "bottom," "inner," "outer," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be understood as limiting this invention.

[0157] The embodiments described above are merely examples of several implementations of the present invention, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the compressor and HVAC equipment of the invention. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention.

Claims

1. A compressor, characterized in that, include: Compressor housing; as well as The pump body structure is located inside the compressor housing and includes at least one cylinder and at least two refrigeration channels; the refrigeration channels pass through the cylinder along its axial direction; the cylinder is fixed relative to the compressor housing.

2. The compressor according to claim 1, characterized in that: The pump body structure further includes an upper silencer cover, an upper bearing, a lower bearing, and a lower silencer cover arranged sequentially along the axial direction. The cylinder is located between the upper bearing and the lower bearing. The upper silencer cover has an air outlet. An upper silencer cavity is formed between the upper silencer cover and the upper bearing. The lower silencer cover and the lower bearing form a lower silencer cavity. A lower exhaust port is provided on the lower bearing, connecting the interior of the cylinder and the lower silencer cavity. Each refrigerant passage passes through the upper bearing, the cylinder, and the lower bearing sequentially along the axial direction of the cylinder and connects the upper silencer cavity and the lower silencer cavity. The cylinder includes a cylinder body and a flange portion sleeved on the outer peripheral side of the cylinder body. The outer peripheral wall of the flange portion is connected to the inner peripheral wall of the compressor housing.

3. The compressor according to claim 1, characterized in that: The inner diameter of the compressor housing is D, and the discharge capacity of the pump structure is V. The relationship between V and D is: 4V / πD² ≥ 1.2 mm.

4. The compressor according to claim 2, characterized in that: The inner diameter of the lower exhaust port is L, the number of refrigerant channels is n, and the inner diameter of each refrigerant channel is d. The relationship between d, n, and L is: 2≤n*d² / L²≤4.

5. The compressor according to claim 4, characterized in that: The upper bearing and the lower bearing are respectively disposed on the upper and lower end faces of the cylinder body. The refrigerant channel passes through the upper bearing, the cylinder body and the lower bearing in sequence. The cylinder body is provided with a compression chamber inside. The radial width of the cylinder body is t. The relationship between t and d is: 2≤t / d≤2.

5.

6. The compressor according to claim 5, characterized in that: The diameter of the upper bearing is greater than or equal to the diameter of the cylinder body, and the diameter of the upper bearing is less than the diameter of the flange; the diameter of the lower bearing is greater than or equal to the diameter of the cylinder body, and the diameter of the lower bearing is less than the diameter of the flange.

7. The compressor according to claim 5, characterized in that: Several refrigerant channels are spaced apart along the circumference of the cylinder body. Each refrigerant channel has a bolt channel on both sides, and the bolt channel passes through the upper muffler cover, the upper bearing, the cylinder body, the lower bearing, and the lower muffler cover in sequence.

8. The compressor according to claim 5, characterized in that: The upper end face of the cylinder body is provided with an upper exhaust notch that communicates with the compression chamber, and the upper bearing is provided with an upper exhaust valve seat that communicates with the upper exhaust notch and the upper muffler chamber; the lower end face of the cylinder body is provided with a lower exhaust notch that communicates with the compression chamber, and the lower bearing is provided with a lower exhaust valve seat that communicates with the lower exhaust notch, and the lower exhaust through hole is connected to the lower exhaust valve seat.

9. The compressor according to claim 5, characterized in that: It also includes a crankshaft, through which the upper muffler cover, upper bearing, cylinder body, lower bearing, and lower muffler cover are sequentially mounted.

10. The compressor according to claim 5, characterized in that: The flange is a circular structure, and several oil return channels are provided through the flange along the axial direction. The oil return channels are distributed at intervals along the circumference of the flange.

11. The compressor according to claim 1, characterized in that: The compressor housing is a sealed container for storing refrigeration oil. The interior of the compressor housing houses an electric component used to drive the pump structure to compress the refrigerant.

12. The compressor according to claim 11, characterized in that: The refrigerant compressed by the pump body structure is at least a natural refrigerant, an HFC refrigerant, or an HFO refrigerant.

13. The compressor according to claim 12, characterized in that: The natural refrigerant is at least one of R290 and CO2, or a mixture thereof; The HFC refrigerant is at least one of R32, R410A, R134a, R404A, and R407C, or a mixture thereof; The HFO type refrigerant is at least one of R454B, R454C, R513A, and R1234yf, or a mixture thereof.

14. The compressor according to claim 11, characterized in that: The refrigeration oil is at least one of POE oil and PVE oil, or a mixture thereof.

15. The refrigerant compressor according to claim 3, characterized in that: The relationship between d, n, and L is: n*d² / L² = 3.

16. The compressor according to claim 5, characterized in that: The relationship between t and d is: t / d = 2.

3.

17. The compressor according to claim 3, characterized in that: The axial height of the cylinder along the compressor housing is H, and H and D satisfy the relationship: D / H < 4.

5.

18. The compressor according to claim 1, characterized in that, Also includes: The stator has a connecting part and a recessed part on its outer peripheral side. The connecting part is connected to the inner peripheral wall of the compressor housing, and the recessed part is in clearance fit with the inner peripheral wall of the compressor housing. The rotor is coaxially disposed inside the stator, and the rotor and the stator form a clearance fit; The pump body structure is located below the stator and the rotor, and the rotor is drivenly connected to the pump body structure; The pump body structure has a discharge capacity of V, the gap area formed between the recess and the compressor housing is S1, a first refrigerant channel is formed between the coil slot of the stator and the coil in the slot, the area of ​​the first refrigerant channel is S2, the gap area formed between the stator and the rotor is S3, a second refrigerant channel is provided in the rotor, the area of ​​the second refrigerant channel is S4, and the total area of ​​the compressor housing for refrigerant to pass through in the axial direction is S. The S satisfies the relationship: S=S1+S2+S3+S4; the V and the S satisfy the relationship: 10mm≤V / S≤15mm.

19. The compressor according to claim 18, characterized in that: The inner diameter of the compressor housing is D, and V and D satisfy the relationship: 4V / πD² ≥ 1.2 mm; where π is the mathematical constant pi.

20. The compressor according to claim 18, characterized in that: The pump body structure has a return oil channel extending through it in the axial direction. The area of ​​the return oil channel is S5. The relationship between S5 and V is: 8mm≤V / S5≤12mm; the relationship between S5 and S is: 0.7≤S / S5≤0.

9.

21. The compressor according to claim 20, characterized in that: The upper bearing, the cylinder, and the lower bearing are coaxially arranged. The cylinder has a compression chamber with openings at both ends. The outer wall of the cylinder is recessed in the radial direction to form an air intake channel that connects to the compression chamber. The upper bearing and the lower bearing are respectively located at the upper and lower openings of the compression chamber.

22. The compressor according to claim 21, characterized in that: The cylinder has several arc-shaped channels distributed along the circumference, passing through both ends of the cylinder, and these arc-shaped channels together form the oil return channel.

23. The compressor according to claim 18, characterized in that: The stator has a plurality of joints evenly distributed on its outer periphery, and a recess is provided between two adjacent joints. The recess is formed by indentation from the outer periphery of the stator, and the arc length of the recess in the circumferential direction is smaller than the arc length of the joint in the circumferential direction.

24. The compressor according to claim 18, characterized in that: The relationship between V and S is: V / S = 12mm.

25. The compressor according to claim 20, characterized in that: The relationship between S5 and V is: V / S5 = 10 mm; the relationship between S5 and S is: S / S5 = 0.

9.

26. The compressor according to claim 1, characterized in that: The upper bearing and the lower bearing are respectively disposed on the upper and lower end faces of the cylinder. The upper bearing has an upper through hole that communicates with the compression chamber along the axial direction, and the lower bearing has a lower through hole that communicates with the compression chamber along the axial direction. The crankshaft includes a long shaft, an eccentric shaft, and a short shaft connected axially in sequence. The long shaft passes through the upper through hole, the eccentric shaft is disposed in the compression chamber, and the short shaft is disposed in the lower through hole. The shortest distance from the axis of the eccentric shaft to the axis of the long shaft is E, and the diameter of the short shaft is d1. E and d1 satisfy the relationship: E / d1≤0.

35. The axial length of the eccentric shaft is H1, and the axial length of the short shaft is h. H1 and h satisfy the relationship: H1 / h≤1.

2. A rotating oil groove is recessed on the inner wall of the lower through hole. The two ends of the rotating oil groove respectively penetrate the two ends of the lower through hole. The radial cross-sectional area of ​​the rotating oil groove is S6. The relationship between S6 and d1 is: 0.05mm≤S6 / d1≤0.1mm.

27. The compressor according to claim 26, characterized in that: The rotation angle of the rotating oil tank is θ, and the height of the rotating oil tank is L1. The relationship between L1 and θ is: 2° / mm≤θ / L1≤4° / mm.

28. The compressor according to claim 27, characterized in that: The relationship between L1 and θ is: θ / L1 = 3° / mm.

29. The compressor according to claim 27, characterized in that: The rotation direction of the rotating oil groove is opposite to the rotation direction of the short shaft.

30. A heating, ventilation, and air conditioning (HVAC) device, characterized in that: Includes the compressor as described in any one of claims 1 to 29.

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