Cylinder, cylinder block, compressor and air conditioner
By designing a double exhaust cylinder on the upper flange and optimizing the valve plates, the exhaust loss problem during high-frequency operation of the rotary compressor was solved, resulting in cost reduction and energy efficiency improvement, while avoiding the need for additional structures.
Patent Information
- Application Number
- CN202411800602.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-09
- Publication Date
- 2025-11-07
- Estimated Expiration
- 2044-12-09
AI Technical Summary
Existing rotary compressors suffer significant exhaust losses during high-frequency operation, leading to increased manufacturing costs and reduced energy efficiency. While the existing dual exhaust port design is effective, it also increases manufacturing costs.
The cylinder adopts a double exhaust cylinder design with an upper flange. The cylinder body is provided with first and second exhaust ports that communicate with the exhaust port of the upper flange. Combined with the first and second valve assemblies, the first valve plate is a pre-pressure relief valve and the second valve plate is the main valve plate. By optimizing the angle and stiffness design, gas backflow and over-compression are reduced, thus reducing equipment costs.
It effectively reduces exhaust pressure loss, improves compressor energy efficiency, reduces equipment manufacturing costs, and avoids the need to add a silencer and flow hole to the lower flange.
Smart Images
Figure CN119267231B_ABST
Abstract
Description
TECHNICAL FIELD
[0001] The present application relates to the technical field of compressor, in particular to a cylinder body, a cylinder, a compressor and an air conditioner. BACKGROUND
[0002] The air conditioner compressor pump body sucks in low-pressure gaseous refrigerant into the cylinder, and gradually compresses it into high-pressure gas, which is discharged through the flange exhaust hole. See Figure 10 From the suction-compression-exhaust process of the refrigerant, the indicated power loss is mainly divided into suction power loss W1, heat transfer, leakage, clearance power loss W2, and exhaust power loss W3. W0 is the theoretical indicated power, and the sum of W0, W1, W2 and W3 is the actual indicated power under the compressor cycle. The exhaust power loss W3 often accounts for the largest proportion of the indicated power loss, which is mainly due to the over-compression phenomenon generated during the discharge of the gas in the cylinder through the flange exhaust hole, thereby causing a large pressure loss.
[0003] The exhaust end of the existing rotary compressor is provided with a first exhaust hole in the upper flange. Correspondingly, the cylinder body is provided with a first exhaust cutout communicating between the compression chamber and the first exhaust hole, and the upper flange is provided with a valve assembly piece assembly to control the exhaust. When the cylinder working displacement is large, the compressor operating frequency is high, or the R290 and other refrigerants with large volume flow are operated at high frequency, only one exhaust hole often causes a large exhaust loss.
[0004] Another existing rotary compressor has two opposite exhaust holes in the upper flange and the lower flange to reduce exhaust loss. Although this design effectively reduces exhaust loss, since part of the refrigerant is discharged from the lower flange, a lower muffler and a flow-through hole are often needed to be added to the lower flange to guide the airflow upward, which greatly increases the manufacturing cost. SUMMARY
[0005] The first object of the present application is to provide a cylinder body for constituting an upper flange double-exhaust cylinder, which reduces the manufacturing cost.
[0006] The second object of the present application is to provide an upper flange double-exhaust cylinder, which reduces the manufacturing cost.
[0007] The third object of the present application is to provide a compressor with reduced manufacturing cost.
[0008] The fourth object of the present application is to provide an air conditioner with reduced manufacturing cost.
[0009] The first object of the present application provides a cylinder body provided with a working chamber, a sliding vane groove, a first exhaust cutout and a second exhaust cutout, the sliding vane groove, the first exhaust cutout and the second exhaust cutout are all communicated with the working chamber, in the axial direction of the cylinder body, the cylinder body includes an upper side, the first exhaust cutout is arranged on the upper side; the second exhaust cutout is arranged on the upper side; in the circumferential direction of the cylinder body, the first exhaust cutout is arranged at a position away from the sliding vane groove relative to the second exhaust cutout.
[0010] As can be seen from the above scheme, the first exhaust cutout and the second exhaust cutout are both arranged on the upper side close to the upper flange, which can cooperate with the upper flange provided with the first exhaust hole and the second exhaust hole to form an upper flange double exhaust cylinder, without the need to additionally provide a lower muffler on the lower flange, and without the need to open a flow-through hole on the lower flange to guide the gas flow upward, thereby reducing the manufacturing cost of the equipment.
[0011] A further scheme is that, in the axial direction of the cylinder body, the diameter of the first exhaust cutout is smaller than the diameter of the second exhaust cutout.
[0012] As can be seen from the above, correspondingly, the diameter of the second exhaust hole on the upper flange is larger than the diameter of the first exhaust hole, so that the first valve plate corresponding to the first exhaust hole and the second valve plate corresponding to the second exhaust hole are opened at the same time during exhaust, but due to the larger diameter of the second exhaust hole, the second valve plate is opened for a longer time, so the second valve plate should be used as the main exhaust valve plate, and the first valve plate is used as the advance pressure relief valve, thereby reducing the over-compression phenomenon of the compression chamber, reducing the exhaust pressure loss under the premise of reducing the manufacturing cost of the equipment, and improving the efficiency of the compressor.
[0013] A further scheme is that, in the axial direction of the cylinder body, the center line of the first exhaust cutout and the center line of the sliding vane groove form a first included angle, the value of the first included angle ranges from 40 degrees to 70 degrees; and / or, in the axial direction of the cylinder body, the center line of the second exhaust cutout and the center line of the sliding vane groove form a second included angle, the value of the second included angle ranges from 5 degrees to 20 degrees.
[0014] As can be seen from the above, under this angle, it is firstly ensured that both exhaust cutouts are located at the exhaust end of the working chamber, and the over-compression phenomenon of exhaust can be effectively reduced. In addition, the gas backflow problem also needs to be considered. Specifically, when both valve assemblies corresponding to the two exhaust holes are opened, if the crankshaft crosses the first exhaust hole in a clockwise direction while the second exhaust hole is still not closed in time, it will cause the first exhaust hole to start corresponding to the low pressure of the suction chamber when the crankshaft continues to rotate forward, and the exhaust pressure of the back of the first exhaust hole corresponding to the muffler is high pressure, which will cause the high pressure refrigerant just discharged in the muffler to flow back to the low pressure suction chamber through the first exhaust hole which is not closed yet, causing refrigerant backflow, which will greatly reduce the refrigeration capacity of the compressor. Under this setting, the first exhaust cutout, the first exhaust hole and the first valve assembly are all closer to the second exhaust hole to form better cooperation, so as to ensure that there is no gas backflow problem during the opening process of the first valve assembly.
[0015] The second object of the present application provides a cylinder comprising a cylinder body and an upper flange, the upper flange is connected with the upper side of the cylinder body along the axial direction of the cylinder body, and the cylinder body adopts the above-mentioned cylinder body; the upper flange comprises a first exhaust hole and a second exhaust hole, the first exhaust hole is communicated with the first exhaust cutout, and the second exhaust hole is communicated with the second exhaust cutout.
[0016] A further scheme is further comprising a first valve assembly and a second valve assembly connected to the upper flange, the first valve assembly comprises a first baffle and a first valve plate, and the second valve assembly comprises a second baffle and a second valve plate; the first valve plate comprises a first deformation part located between the first baffle and the first exhaust hole, and the second valve plate comprises a second deformation part located between the second baffle and the second exhaust hole; the diameter of the second exhaust hole is larger than the diameter of the first exhaust hole, and the rigidity of the second valve plate is greater than the rigidity of the first valve plate.
[0017] As can be seen from the above scheme, since the first valve plate and the second valve plate are opened at the same time during exhaust, but the second valve plate is opened for a longer time, the second valve plate should be used as the main exhaust valve plate, and the first valve plate is an early pressure relief valve, which reduces the over-compression phenomenon of the compression chamber, and the rigidity of the second valve plate should be greater than the rigidity of the first valve plate, and at the same time, the diameter of the second exhaust hole should be greater than the diameter of the first exhaust hole.
[0018] A further scheme is that the first deformation part comprises a first waist part and a first head part arranged in sequence along the length direction of the first deformation part, and the first head part is located between the first baffle and the first exhaust hole; the second deformation part comprises a second waist part and a second head part arranged in sequence along the length direction of the second deformation part, and the second head part is located between the second baffle and the second exhaust hole; the first thickness t1 of the first valve plate, the first width b1 of the first waist part, the first diameter d1 of the first head part, the first length l1 of the first deformation part, the second thickness t2 of the second valve plate, the second width b2 of the second waist part, the second diameter d2 of the second head part, and the second length l2 of the second deformation part satisfy: In addition, a further scheme is that the first diameter d3 of the first exhaust hole, the second diameter d4 of the second exhaust hole, the first lift h1 of the first baffle, and the second lift h2 of the second baffle satisfy: .
[0019] As can be seen from the above, the first length l1 and the second length l2 refer to the distance from the vertex of the head part of the valve plate to the starting point of the valve plate constrained by the baffle; when the waist part of a valve plate is in the shape of a variable cross-section, the first width b1 and the second width b2 respectively refer to the width of the narrowest part of the waist part. Since the first exhaust hole serves as an auxiliary exhaust hole for the second exhaust hole, better, in addition to designing the circumferential distance of the first exhaust hole and the second exhaust hole, the parameters are also relatedly designed according to the displacement requirements of the first exhaust hole and the second exhaust hole, and according to the size and rigidity of the first valve plate and the second valve plate, etc., so that the two exhaust holes can produce better coordination effect.
[0020] Further, the first valve plate comprises a first base and a first wear-resistant coating part, and the first wear-resistant coating part is arranged towards the first baffle plate; and / or the second valve plate comprises a second base and a second wear-resistant coating part, and the second wear-resistant coating part is arranged towards the second baffle plate.
[0021] From the above, in order to face the over-compression phenomenon, the wear-resistant coating is combined to improve the wear resistance of the valve plate, and the reliability of the valve assembly plate is further ensured.
[0022] The compressor provided by the third object of the present application comprises the cylinder.
[0023] The air conditioner provided by the fourth object of the present application comprises the compressor, and the compressor adopts the compressor. BRIEF DESCRIPTION OF DRAWINGS
[0024] Figure 1 It is an axial view of the cylinder body, the crankshaft and the sliding vane in the first embodiment of the cylinder of the present application.
[0025] Figure 2 It is an axial view of the upper flange in the first embodiment of the cylinder of the present application.
[0026] Figure 3 It is a sectional view of the upper flange and the first valve assembly in the first embodiment of the cylinder of the present application.
[0027] Figure 4 It is a structural view of the first valve plate in the first embodiment of the cylinder of the present application.
[0028] Figure 5 It is a sectional view of the upper flange and the second valve assembly in the first embodiment of the cylinder of the present application.
[0029] Figure 6 It is a structural view of the second valve plate in the first embodiment of the cylinder of the present application.
[0030] Figure 7 It is a sectional view of the second valve plate in the first embodiment of the cylinder of the present application.
[0031] Figure 8 It is a sectional view of the second valve plate in the second embodiment of the cylinder of the present application.
[0032] Figure 9 It is a structural view of the first valve plate in the third embodiment of the cylinder of the present application.
[0033] Figure 10 It is a PV indication loss diagram of the prior art compressor.
[0034] Figure 11 It is a PV indication loss diagram of the compressor embodiment of the present application. DETAILED DESCRIPTION
[0035] Cylinder first embodiment
[0036] Referring to Figure 1 and Figure 2 , the cylinder comprises an upper flange 1, a cylinder body 2, a crankshaft 3 and a sliding vane 4, of course, also comprises a lower flange which is not shown. Figure 1 and Figure 2 The views shown are all top views, that is, axial views from top to bottom. The upper flange 1 is connected with the upper side of the cylinder body 2 along the axial direction of the cylinder body 2, the sliding vane 4 is installed in the sliding vane groove 400 of the cylinder body 2, and the crankshaft 3 is arranged in the working chamber 200 of the cylinder body 2.
[0037] The cylinder body 2 is provided with a working chamber 200, a sliding vane groove 400, a first exhaust cutout 201 and a second exhaust cutout 202, and the sliding vane groove 400, the first exhaust cutout 201 and the second exhaust cutout 202 are all communicated with the working chamber 200. Further, the working chamber 200 is a circular space in the center of the cylinder body 2, the sliding vane groove 400 extends along the radial direction of the working chamber 200 and is communicated with the working chamber 200, and the center line 4001 of the sliding vane groove 400 coincides with the center point of the working chamber 200.
[0038] In the axial direction of the cylinder body 2, the cylinder body 2 comprises an upper side, Figure 1 The side shown is the upper side of the cylinder body 2; the first exhaust cutout 201 and the second exhaust cutout 202 are both arranged on the upper side of the cylinder body 2, the intake side of the first exhaust cutout 201 and the second exhaust cutout 202 is communicated with the working chamber 200 along the radial direction of the working chamber 200, and the exhaust side of the first exhaust cutout 201 and the second exhaust cutout 202 is communicated with the exhaust structure of the upper flange 1 along the axial direction of the working chamber 200 and upward.
[0039] Referring to Figure 1 , the first exhaust cutout 201 and the second exhaust cutout 202 both have a circular arc profile, and in fact, the circular arc lines of the first exhaust cutout 201 and the second exhaust cutout 202 are consistent with the diameter and center of the circumferential line of the corresponding exhaust hole on the upper flange 1 to ensure the close butt joint between the cutout and the exhaust hole.
[0040] Referring to Figure 1In the circumferential direction of the cylinder body 2, the first exhaust cutout 201 is arranged at a position away from the sliding vane groove 400 relative to the second exhaust cutout 202, specifically, the first exhaust cutout 201, the second exhaust cutout 202 and the sliding vane groove 400 are arranged in sequence along the clockwise direction. Among them, in the axial direction of the cylinder body 2, the center line of the first exhaust cutout 201 forms a first included angle a with the center line of the sliding vane groove 400, and the value of the first included angle a is 40-70 degrees; in the axial direction of the cylinder body 2, the center line of the second exhaust cutout 202 forms a second included angle b with the center line of the sliding vane groove 400, and the value of the second included angle b is 5-20 degrees. Among them, the center line of the first exhaust cutout 201 is the connecting line from the center of the arc line of the first exhaust cutout 201 to the center point of the working chamber 200, and the center line of the second exhaust cutout 202 is the connecting line from the center of the arc line of the second exhaust cutout 202 to the center point of the working chamber 200. The first exhaust cutout 201, the first exhaust hole 1011 and the first valve assembly under this angle setting are close enough to the second exhaust hole 1021 to form better cooperation to ensure that there is no gas backflow problem during the opening process of the first valve assembly. In addition, in the axial direction of the cylinder body 2, the caliber of the first exhaust cutout 201 is smaller than the caliber of the second exhaust cutout 202.
[0041] Referring to Figure 2 The upper surface of the upper flange 1 is provided with a first groove 101 and a second groove 102 which are recessed downward and extend along a straight line, the first groove 101 and the second groove 102 form an included angle, the two ends of the extension of the first groove 101 are respectively provided with a first exhaust hole 1011 and a first rivet hole 1012, and the two ends of the extension of the second groove 102 are respectively provided with a second exhaust hole 1021 and a first rivet hole 1022, the first exhaust hole 1011 and the second exhaust hole 1021 penetrate the upper flange 1 along the axial direction of the upper flange 1, and the axial direction of the upper flange 1 is consistent with the axial direction of the cylinder. Among them, the first diameter d3 of the first exhaust hole 1011 is smaller than the second diameter d4 of the second exhaust hole 1021. In addition, Figure 1 The middle cylinder body 2 and Figure 2 The middle cylinder body 2 and the upper flange 1 can be assembled in the axial direction without adjusting the position in the circumferential direction, that is, the azimuth angles of the two are consistent. It can be seen that the first exhaust hole 1011 is located at the same position as the first exhaust cutout 201, the second exhaust hole 1021 is located at the same position as the second exhaust cutout 202, and after the cylinder body 2 and the upper flange 1 are assembled, the first exhaust hole 1011 communicates with the first exhaust cutout 201, and the second exhaust hole 1021 communicates with the second exhaust cutout 202.
[0042] Referring to Figure 3 and Figure 4, the cylinder further comprises a first valve assembly and a second valve assembly connected to the upper flange 1. The first valve assembly comprises a first baffle plate 6 and a first valve piece 5, the first valve piece 5 comprises a first fixed part 51 and a first deformed part 52, the first deformed part 52 further comprises a first waist part 502 and a first head part 503 arranged in sequence along the length direction of the first deformed part 52, that is, the first valve piece 5 comprises the first fixed part 51, the first waist part 502 and the first head part 503 connected in sequence along the length direction of the first valve piece 5. The first rivet 71 passes through the first baffle plate 6, the first fixed part 51 and the first rivet hole 1012 in sequence to connect the three, and the first head part 503 on the first deformed part 52 is located between the first baffle plate 6 and the first exhaust hole 1011.
[0043] Referring to Figure 5 and Figure 6 , the second valve assembly comprises a second baffle plate 9 and a second valve piece 8, the second valve piece 8 comprises a second fixed part 81 and a second deformed part 82, the second deformed part 82 further comprises a second waist part 802 and a second head part 803 arranged in sequence along the length direction of the second deformed part 82, that is, the second valve piece 8 comprises the second fixed part 81, the second waist part 802 and the second head part 803 connected in sequence along the length direction of the second valve piece 8. The second rivet 72 passes through the second baffle plate 9, the second fixed part 81 and the second rivet hole 1022 in sequence to connect the three, and the second head part 803 on the second deformed part 82 is located between the second baffle plate 9 and the second exhaust hole 1021.
[0044] In this way, the cylinder body 2 sets the first exhaust cutout 201 and the second exhaust cutout 202 on the upper side close to the upper flange 1, cooperates with the first exhaust hole 1011 and the second exhaust hole 1021 of the upper flange 1 and the first valve assembly and the second valve assembly to form an upper flange double exhaust cylinder, and no longer needs to add a lower silencer on the lower flange or open a flow hole on the lower flange to guide the airflow upward, thereby reducing the equipment manufacturing cost, reducing the exhaust pressure loss and improving the compressor efficiency.
[0045] Referring to Figures 3 to 6 , the first thickness t1 of the first valve piece 5, the first width b1 of the first waist part 502, the first diameter d1 of the first head part 503, the first length l1 of the first deformed part 52, the second thickness t2 of the second valve piece 8, the second width b2 of the second waist part 802, the second diameter d2 of the second head part 803, and the second length l2 of the second deformed part 82 satisfy:
[0046]
[0047] The first diameter d3 of the first exhaust hole 1011, the second diameter d4 of the second exhaust hole 1021, the first lift h1 of the first baffle plate 6, and the second lift h2 of the second baffle plate 9 satisfy:
[0048]
[0049] Wherein, the first lift h1 of the first baffle 6 refers to the distance from the upper surface of the first deformation part 52 in the horizontal state to the lower surface of the first baffle 6 at the position of the center line of the first exhaust hole 1011, and the second lift h2 of the second baffle 9 refers to the distance from the upper surface of the second deformation part 82 in the horizontal state to the lower surface of the second baffle 9 at the position of the center line of the second exhaust hole 1021.
[0050] When the waist part of one valve plate is in the variable cross-section shape, the first width b1 and the second width b2 respectively refer to the width of the narrowest part of the waist part. Since the first exhaust hole 1011 is the auxiliary exhaust hole of the second exhaust hole 1021, preferably, in addition to the design of the circumferential distance between the first exhaust hole 1011 and the second exhaust hole 1021, the correlation design of various parameters is also made according to the displacement requirements of the first exhaust hole 1011 and the second exhaust hole 1021, and according to the size and stiffness of the first valve plate 5 and the second valve plate 8, so that the two exhaust holes can produce better coordination effect.
[0051] In addition, since the first valve plate 5 and the second valve plate 8 are opened at the same time during exhaust, but the second valve plate 8 is opened for a longer time due to the larger hole diameter, the second valve plate 8 should be the main exhaust valve plate, and the first valve plate 5 is the advance pressure relief valve, which can reduce the over-compression phenomenon of the compression chamber, and the stiffness of the second valve plate 8 is greater than that of the first valve plate 5.
[0052] Referring to Figure 7 , the second valve plate 8 comprises a second base 88 and a second wear-resistant coating part 89, and the second wear-resistant coating part 89 is arranged towards the second baffle 9. Similarly, the first valve plate comprises a first base and a first wear-resistant coating part, and the first wear-resistant coating part is arranged towards the first baffle. The second wear-resistant coating part 89 and the first wear-resistant coating part are both coated with nitriding, nitriding sulfur or nitriding molybdenum, etc. Under this arrangement, the second wear-resistant coating part 89 and the first wear-resistant coating part both only contain one wear-resistant layer.
[0053] Referring to Figure 11 and comparing Figure 10 , the cylinder adopting the embodiment can effectively reduce the exhaust power loss W3.
[0054] The air conditioner of the application comprises a compressor, and the compressor of the application comprises the cylinder of the embodiment. Of course, the compressor also comprises a shell and a motor, and both the shell and the motor can be implemented by using the prior art.
[0055] Second embodiment of the cylinder
[0056] Referring to Figure 8In the embodiment, the second valve plate 8' comprises a second base 88' and a second wear-resistant coating part 89', the second wear-resistant coating part 89' adopts a DLC diamond-like carbon film coating, and the second wear-resistant coating part 89' comprises a connecting layer 891, a supporting layer 892 and a functional wear-resistant layer 893 arranged outwardly from the second base 88' in sequence.
[0057] The first wear-resistant coating part of the first valve plate also adopts a DLC diamond-like carbon film coating.
[0058] Cylinder third embodiment
[0059] Referring to Figure 9 In the embodiment, when the waist part of the first valve plate or the second valve plate is in a variable cross-section shape, the first width b1 or the second width b2 respectively refers to the width of the narrowest part of the waist part.
[0060] Finally, it should be emphasized that the above description is only the preferred embodiment of the present application, and is not intended to limit the present application. For those skilled in the art, the present application can have various changes and modifications, and any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.
Claims
1. A cylinder body, comprising a working chamber, a sliding vane slot, a first exhaust cutout and a second exhaust cutout, the sliding vane slot, the first exhaust cutout and the second exhaust cutout being communicated with the working chamber, the cylinder body comprising an upper side in an axial direction of the cylinder body, and the first exhaust cutout being arranged on the upper side; characterized in that: the second exhaust cutout is arranged on the upper side; in a circumferential direction of the cylinder body, the first exhaust cutout is arranged at a position away from the sliding vane slot relative to the second exhaust cutout; and a center line of the first exhaust cutout forms a first included angle with a center line of the sliding vane slot in the axial direction of the cylinder body, and the first included angle ranges from 40 degrees to 70 degrees. 2.The cylinder body according to claim 1, characterized in that: a caliber of the first exhaust cutout is smaller than a caliber of the second exhaust cutout in the axial direction of the cylinder body. 3.The cylinder body according to claim 1 or 2, characterized in that: a center line of the second exhaust cutout forms a second included angle with the center line of the sliding vane slot in the axial direction of the cylinder body, and the second included angle ranges from 5 degrees to 20 degrees. 4.A cylinder, comprising a cylinder body and an upper flange connected with the upper side of the cylinder body in an axial direction of the cylinder body, characterized in that: the cylinder body is the cylinder body according to any one of claims 1 to 3; and the upper flange comprises a first exhaust hole communicated with the first exhaust cutout and a second exhaust hole communicated with the second exhaust cutout. 5.The cylinder according to claim 4, characterized in that: further comprising a first valve assembly and a second valve assembly connected with the upper flange, the first valve assembly comprising a first baffle and a first valve plate, and the second valve assembly comprising a second baffle and a second valve plate; the first valve plate comprises a first deformation portion between the first baffle and the first exhaust hole, and the second valve plate comprises a second deformation portion between the second baffle and the second exhaust hole; a caliber of the second exhaust hole is larger than a caliber of the first exhaust hole, and a rigidity of the second valve plate is greater than a rigidity of the first valve plate. 6.The cylinder according to claim 5, characterized in that: the first deformation portion comprises a first waist portion and a first head portion arranged in sequence along a length direction of the first deformation portion, and the first head portion is located between the first baffle and the first exhaust hole; the second deformation portion comprises a second waist portion and a second head portion arranged in sequence along a length direction of the second deformation portion, and the second head portion is located between the second baffle and the second exhaust hole; and a first thickness t1 of the first valve plate, a first width b1 of the first waist portion, a first diameter d1 of the first head portion, a first length l1 of the first deformation portion, a second thickness t2 of the second valve plate, a second width b2 of the second waist portion, a second diameter d2 of the second head portion, and a second length l2 of the second deformation portion satisfy: t1 < b1 < d1 < l1 < t2 < b2 < d2 < l2. 7.The cylinder according to claim 6, characterized in that: 。 The first diameter d3 of the first exhaust hole, the second diameter d4 of the second exhaust hole, the first lift h1 of the first baffle, and the second lift h2 of the second baffle satisfy: 。 8. The cylinder according to any one of claims 5 to 7, characterized in that: The first valve plate comprises a first base and a first wear-resistant coating part, and the first wear-resistant coating part is arranged towards the first baffle; and / or, The second valve plate comprises a second base and a second wear-resistant coating part, and the second wear-resistant coating part is arranged towards the second baffle.
9. Compressor comprising a cylinder, characterized in that The compressor adopts the cylinder according to any one of claims 4 to 8.
10. An air conditioner comprising a compressor, characterized by The compressor adopts the compressor according to claim 9.
Citation Information
Patent Citations
Rotary compressor and compression mechanism thereof
CN105201830A
Compressor and upper flange assembly thereof
CN214170836U