Pump body assembly, compressor and refrigeration equipment

Abstract

The pump body assembly is provided with a low-pressure compression cavity, a middle cavity and a high-pressure compression cavity, a first exhaust port of the low-pressure compression cavity communicates with an air suction port of the high-pressure compression cavity through the middle cavity, the working volume of the low-pressure compression cavity is V1, the minimum through-flow area of the first exhaust port is S1, and the working volume of the high-pressure compression cavity is V2, the minimum through-flow area of the second exhaust port is S2, the lift height of the first lift limiter is H1, the lift height of the second lift limiter is H2, the diameter of the first head part is D1, the minimum distance between the circle center of the first head part and the connecting position where the first fixing part is connected to the first valve seat is L1, the minimum width of the first connecting part is F1, and the diameter of the second head part is D2; the minimum distance between the circle center of the second head part and the connecting position of the second fixing part and the second valve seat is L2, the minimum width of the second connecting part is F2, and U is equal to (V1 * S1 * H1 * L1 * D2 * F2) / (V2 * S2 * H2 * L2 * D1 * F1), and U is larger than or equal to 0.37 and smaller than or equal to 8.4, so that the performance of the compressor is improved.

Description

Technical Field

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

[0002] At present, the pump body assembly adopts multi-stage compression technology to evenly distribute the pressure ratio of each stage of the compression assembly, so that the compression assembly is within a relatively reasonable pressure ratio range, thereby improving the volumetric efficiency of the compressor. The existing pump body assembly is provided with a low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber is communicated with the suction port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure compression chamber is temporarily stored in the intermediate chamber for transition and then is sucked into the high-pressure compression chamber for secondary compression. The exhaust resistance of the low-pressure compression chamber and the high-pressure compression chamber of the existing pump body assembly is relatively large, which affects the performance of the compressor. Summary of the Invention

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. For this purpose, the present invention provides a pump body assembly, which can improve the performance of the compressor.

[0004] The present invention also provides a compressor having the above-mentioned pump body assembly.

[0005] The present invention also provides a refrigeration device having the above-mentioned compressor.

[0006] The pump body assembly according to the first aspect embodiment of the present invention includes:

[0007] It is provided with a low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber. The first exhaust port of the low-pressure compression chamber is communicated with the suction port of the high-pressure compression chamber through the intermediate chamber. The pump body assembly includes:

[0008] A first exhaust assembly, including a first valve seat, a first valve plate and a first lift limiter. The first valve seat is provided with the first exhaust port. The first valve plate includes a first head, a first connecting portion and a first fixing portion connected in sequence. The first head is used to open or close the first exhaust port. The first fixing portion and the first lift limiter are both connected to the first valve seat. The first lift limiter is located on the side of the first valve plate away from the first valve seat;

[0009] A second exhaust assembly, including a second valve seat, a second valve plate and a second lift limiter. The second valve seat is provided with a second exhaust port communicating with the high-pressure compression chamber. The second valve plate includes a second head, a second connecting portion and a second fixing portion connected in sequence. The second head is used to open or close the second exhaust port. The second fixing portion and the second lift limiter are both connected to the second valve seat. The second lift limiter is located on the side of the second valve plate away from the second valve seat;

[0010] Among them, the working volume of the low-pressure compression chamber is V1, the minimum flow-through area of the first exhaust port is S1, the working volume of the high-pressure compression chamber is V2, the minimum flow-through area of the second exhaust port is S2, the lift height of the first lift limiter is H1, the lift height of the second lift limiter is H2, the diameter of the first head is D1, the minimum distance between the center of the first head and the connection position where the first fixing part is connected to the first valve seat is L1, the minimum width of the first connecting part is F1, the diameter of the second head is D2, the minimum distance between the center of the second head and the connection position where the second fixing part is connected to the second valve seat is L2, the minimum width of the second connecting part is F2, and it satisfies: U = (V1 × S1 × H1 × L1 × D2 × F2) / (V2 × S2 × H2 × L2 × D1 × F1), and 0.37 ≤ U ≤ 8.4.

[0011] The pump body assembly according to the embodiment of the present invention has at least the following beneficial effects:

[0012] When the pump body assembly is working, the refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber from the suction port of the low-pressure compression chamber. The refrigerant completes the first-stage compression in the low-pressure compression chamber. Under the action of the gas pressure in the low-pressure compression chamber, the first head opens the first exhaust port and the first head abuts against the first lift limiter. The refrigerant is discharged through the first exhaust port into the first cavity. At this time, the first head closes the first exhaust port. The refrigerant in the first cavity is sucked into the high-pressure compression chamber from the suction port of the high-pressure compression chamber. The refrigerant completes the second-stage compression in the high-pressure compression chamber. Under the action of the gas pressure in the high-pressure compression chamber, the second head opens the second exhaust port and the second head abuts against the second lift limiter. The refrigerant is discharged through the second exhaust port. On the one hand, the low-pressure compression chamber and the high-pressure compression chamber are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. On the other hand, it can effectively reduce the suction pulsation and exhaust pulsation of the pump body assembly, thereby improving the performance of the compressor. Since the diameter of the first head is D1, the minimum distance between the center of the first head and the connection position where the first fixing part is connected to the first valve seat is L1, the diameter of the second head is D2, the minimum distance between the center of the second head and the connection position where the second fixing part is connected to the second valve seat is L2, the working volume of the low-pressure compression chamber is V1, the minimum flow area of the first exhaust port is S1, the working volume of the high-pressure compression chamber is V2, the minimum flow area of the second exhaust port is S2, the lift height of the first lift limiter is H1, the lift height of the second lift limiter is H2, the minimum width of the first connecting part is F1, and the minimum width of the second connecting part is F2, which satisfy: U = (V1 × S1 × H1 × L1 × D2 × F2) / (V2 × S2 × H2 × L2 × D1 × F1), 0.37 ≤ U ≤ 8.4. When U is less than 0.At 37°C, the working volume V2 of the high-pressure compression chamber is too large, which is equivalent to the working volume V1 of the low-pressure compression chamber being too small. The suction volume of the high-pressure compression chamber is insufficient, and the heating capacity is insufficient. The flow area S2 of the second exhaust port is too large, resulting in the gas in the high-pressure compression chamber being discharged before reaching the designed pressure. The actual exhaust volume of the high-pressure compression chamber decreases, and the volumetric efficiency of the compressor decreases. The lift height H2 of the second lift limiter is too large, resulting in a decrease in gas flow velocity, which may form eddies or backflows, increasing the refrigerant flow resistance. The minimum distance L2 between the center of the second head and the connection position of the second fixing part to the second valve seat is too large, the diameter D2 of the second head is too small, and the minimum width F2 of the second connecting part is too small, all of which result in too small stiffness of the valve plate, and the gas in the compression chamber is discharged before reaching the designed pressure. The actual exhaust volume of the compression chamber decreases, and the volumetric efficiency of the compressor decreases. Under the combined action of the working volume V2 of the high-pressure compression chamber being too large, the flow area S2 of the second exhaust port being too large, the lift height H2 of the second lift limiter being too large, the minimum distance L2 between the center of the second head and the connection position of the second fixing part connected to the second valve seat being too large, the diameter D2 of the second head being too small, and the minimum width F2 of the second connecting part being too small, the actual exhaust volume of the high-pressure compression chamber decreases, and the performance of the compressor deteriorates; when U is greater than 8.At 4 o'clock, the working volume V2 of the high-pressure compression chamber is too small, and the high-pressure compression chamber cannot completely consume the refrigerant discharged from the low-pressure compression chamber, resulting in excessive performance and a decrease in the volumetric efficiency of the compressor. The flow area S2 of the second exhaust port is too small, resulting in an increase in gas flow resistance, and the gas in the high-pressure compression chamber cannot be discharged in time, causing the exhaust pressure to rise and the performance of the compressor to decrease. The lift height H2 of the second lift limiter is too small, resulting in too small an opening angle of the second valve plate, and the gas in the high-pressure compression chamber cannot be discharged in time, increasing the power consumption of the compressor and reducing the performance of the compressor. The minimum distance L2 between the center of the second head and the connection position where the second fixed part is connected to the second valve seat, the large diameter D2 of the second head, and the large minimum width F2 of the second connecting part all result in too large a stiffness of the valve plate. The resistance to be overcome for the second valve plate to open is too large, increasing the exhaust resistance of the high-pressure compression chamber. Under the combined action of the small working volume V2 of the high-pressure compression chamber, the small flow area S2 of the second exhaust port, the small lift height H2 of the second lift limiter, the small minimum distance L2 between the center of the second head and the connection position where the second fixed part is connected to the second valve seat, the large diameter D2 of the second head, and the large minimum width F2 of the second connecting part, the exhaust resistance of the high-pressure compression chamber increases and the performance of the compressor decreases. Therefore, by reasonably designing the relationship between the diameter D1 of the first head, the minimum distance L1 between the center of the first head and the connection position where the first fixed part is connected to the first valve seat, the diameter D2 of the second head, the minimum distance L2 between the center of the second head and the connection position where the second fixed part is connected to the second valve seat, the working volume V1 of the low-pressure compression chamber, the minimum flow area S1 of the first exhaust port, the working volume V2 of the high-pressure compression chamber, the minimum flow area S2 of the second exhaust port, the lift height H1 of the first lift limiter, the lift height H2 of the second lift limiter, the minimum width F1 of the first connecting part, and the minimum width F2 of the second connecting part, the exhaust volume of the high-pressure compression chamber can be increased, and the exhaust resistance of the high-pressure compression chamber can be reduced, thereby improving the performance of the compressor.

[0013] According to some embodiments of the present invention, the lift height H1 of the first lift limiter is less than or equal to the lift height H2 of the second lift limiter.

[0014] According to some embodiments of the present invention, the first lift limiter includes a first mounting portion and a first limiting portion connected to the first mounting portion. The first mounting portion is connected to the first valve seat. The first limiting portion is correspondingly arranged with the first head to limit the first head. The thickness of the first mounting portion along the axial direction of the pump body assembly is T1. The second lift limiter includes a second mounting portion and a second limiting portion connected to the second mounting portion. The second mounting portion is connected to the second valve seat. The second limiting portion is correspondingly arranged with the second head to limit the second head. The thickness of the second mounting portion along the axial direction of the pump body assembly is T2, satisfying: T2≥T1.

[0015] According to some embodiments of the present invention, the thickness of the first valve plate is T3, and the thickness of the second valve plate is T4, satisfying: 1.3≤T4 / T3≤1.7.

[0016] According to some embodiments of the present invention, the ratio of the working volume of the high-pressure compression chamber to the volume of the low-pressure compression chamber is V2 / V1, satisfying: 0.4≤V2 / V1≤0.8.

[0017] According to some embodiments of the present invention, the pump body assembly further includes a lower bearing, a first cylinder, a partition assembly, a second cylinder, and an upper bearing connected in sequence. The lower bearing, the first cylinder, and the partition assembly enclose to form the low-pressure compression chamber. The upper bearing, the second cylinder, and the partition assembly enclose to form the high-pressure compression chamber. The partition assembly is provided with a first cavity of the intermediate chamber. At least one of the partition assembly and the lower bearing is provided with the first valve seat, and the upper bearing is provided with the second valve seat.

[0018] According to some embodiments of the present invention, the partition assembly and the lower bearing are respectively provided with the first valve seat, and the thickness of the first valve plate located on the partition assembly is greater than or equal to the thickness of the first valve plate located on the lower bearing.

[0019] According to some embodiments of the present invention, the pump body assembly further includes a lower silencer. The lower silencer is arranged on the side of the lower bearing away from the first cylinder. The lower silencer and the lower bearing enclose to form a second cavity of the intermediate chamber. The lower bearing is provided with the first valve seat. The first cylinder is provided with a communication channel. Two ends of the communication channel are respectively communicated with the first cavity and the second cavity. The first exhaust port located on the lower bearing discharges gas to the second cavity.

[0020] According to some embodiments of the present invention, the partition assembly includes a first partition and a second partition that are oppositely arranged along the axial direction of the pump body assembly. The first partition and the second partition enclose to form the first cavity. The first partition is connected to the first cylinder, and the second partition is connected to the second cylinder.

[0021] The compressor according to the second aspect embodiment of the present invention includes the pump body assembly described in the above embodiments.

[0022] The refrigeration device according to the third aspect embodiment of the present invention includes the compressor described in the above embodiments.

[0023] The additional aspects and advantages of the present invention will be partially given in the following description, partially become apparent from the following description, or be understood through the practice of the present invention. Description of the Drawings

[0024] The following further describes the present invention in conjunction with the drawings and embodiments, where:

[0025] Figure 1 It is a cross-sectional view of a pump body assembly according to an embodiment of the present invention;

[0026] Figure 2 It is a top view of a pump body assembly according to an embodiment of the present invention, with the upper muffler hidden in the figure;

[0027] Figure 3 is Figure 2 The cross-sectional view taken along line A-A in;

[0028] Figure 4 is Figure 3 The partial enlarged view of part B in;

[0029] Figure 5 is Figure 3 The partial enlarged view of part C in;

[0030] Figure 6 is Figure 3 The partial enlarged view of part E in;

[0031] Figure 7 It is a top view of a first valve plate according to an embodiment of the present invention;

[0032] Figure 8 It is a top view of a first valve plate according to another embodiment of the present invention;

[0033] Figure 9 It is a top view of a second valve plate according to an embodiment of the present invention;

[0034] Figure 10 It is a top view of a second valve plate according to another embodiment of the present invention

[0035] Figure 11 Relationship diagram of U and compressor COP according to an embodiment of the present invention.

[0036] Reference numerals in the attached drawings:

[0037] Axis O1, first arc edge Y1, second arc edge Y2, low-pressure compression chamber 110, intermediate chamber 120, first cavity 121, second cavity 122, communication channel 123, high-pressure compression chamber 130, third cavity 140;

[0038] First valve seat 210, first exhaust port 211, first valve plate 220, first head 221, first connecting portion 222, first fixing portion 223, first lift limiter 230, first mounting portion 231, first limiting portion 232;

[0039] Second valve seat 310, second exhaust port 311, second valve plate 320, second head 321, second connecting portion 322, second fixing portion 323, second lift limiter 330, second mounting portion 331, second limiting portion 332;

[0040] Lower bearing 410, first cylinder 420, partition assembly 430, first partition 431, second partition 432, second cylinder 440, upper bearing 450, lower silencer 460, crankshaft 470, first eccentric portion 471, second eccentric portion 472, upper silencer 480, first piston 491, second piston 492. Detailed implementation manners

[0041] The embodiments of the present invention will be described in detail below. Examples of the embodiments are shown in the drawings, where the same or similar reference numerals indicate the same or similar elements or elements with the same or similar functions throughout. The embodiments described below with reference to the drawings are exemplary and are only used to explain the present invention and should not be construed as a limitation of the present invention.

[0042] In the description of the present invention, it should be understood that the orientation or positional relationship indicated by terms such as up and down is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present invention.

[0043] In the description of the present invention, "a plurality of" means more than two. If there is a description of "first" and "second", it is only for the purpose of distinguishing technical features and should not be construed as indicating or implying relative importance or implicitly indicating the number of the indicated technical features or the sequence of the indicated technical features.

[0044] In the description of the present invention, unless otherwise clearly defined, terms such as "set", "installed", "connected", etc. should be understood in a broad sense, and those skilled in the art can reasonably determine the specific meanings of the above terms in the present invention in combination with the specific content of the technical solution.

[0045] In the related art, the pump body assembly adopts multi-stage compression technology to evenly distribute the pressure ratio of each stage of the compression assembly, so that the compression assembly is within a relatively reasonable pressure ratio range, thereby improving the volumetric efficiency of the compressor. The existing pump body assembly is provided with a low-pressure compression chamber, an intermediate chamber, and a high-pressure compression chamber. The exhaust port of the low-pressure compression chamber is communicated with the suction port of the high-pressure compression chamber through the intermediate chamber. The refrigerant compressed in the low-pressure compression chamber is temporarily stored in the intermediate chamber for transition and then sucked into the high-pressure compression chamber for secondary compression. The exhaust resistance of the low-pressure compression chamber and the high-pressure compression chamber of the existing pump body assembly is relatively large, which affects the performance of the compressor. It can be understood that generally, the pressure ratio of the compressor is the ratio of the inlet and outlet pressures, but there are pressure ratios in different compression chambers here.

[0046] Refer to Figures 1 to 3 , Figure 1 is a schematic cross-sectional view of a pump body assembly according to an embodiment of the present invention, Figure 2 is a top view of a pump body assembly according to an embodiment of the present invention, Figure 3 is Figure 2 the cross-sectional view taken along line A-A in Figure 2The upper muffler 480 is hidden therein. As shown in the figure, for a pump body assembly according to an embodiment of the present invention, the pump body assembly includes a crankshaft 470, a lower bearing 410, a first cylinder 420, a partition assembly 430, a second cylinder 440, an upper bearing 450, a first exhaust assembly, and a second exhaust assembly. The crankshaft 470 includes a first eccentric portion 471 and a second eccentric portion 472 that are axially spaced along the crankshaft 470. Axially along the crankshaft 470, the lower bearing 410 is connected to the lower end face of the first cylinder 420, and the partition assembly 430 is connected to the upper end face of the first cylinder 420. The lower bearing 410, the first cylinder 420, and the partition assembly 430 enclose a low-pressure compression chamber 110. The first eccentric portion 471 is rotatably disposed in the low-pressure compression chamber 110. The upper bearing 450 is connected to the upper end face of the second cylinder 440, and the partition assembly 430 is connected to the lower end face of the second cylinder 440. The upper bearing 450, the second cylinder 440, and the partition assembly 430 enclose a high-pressure compression chamber 130. The second eccentric portion 472 is rotatably disposed in the high-pressure compression chamber 130. The partition assembly 430 and the lower bearing 410 are respectively provided with a first valve seat 210. The first valve seat 210 is provided with a first exhaust port 211, that is, the low-pressure compression chamber 110 adopts a double-exhaust scheme. The upper bearing 450 is provided with a second valve seat 310. The second valve seat 310 is provided with a second exhaust port 311. The partition assembly 430 is provided with a first cavity 121 of an intermediate cavity 120. The first exhaust port 211 communicates with the suction port of the high-pressure compression chamber 130 through the intermediate cavity 120. The first exhaust assembly corresponds to the first exhaust port 211 one by one. The first exhaust assembly includes a first valve plate 220 and a first lift limiter 230. The first valve plate 220 includes a first head 221, a first connecting portion 222, and a first fixing portion 223. One end of the first connecting portion 222 is connected to the first head 221, and the other end of the first connecting portion 222 is connected to the first fixing portion 223. The first fixing portion 223 is fixedly connected to the first valve seat 210. The first head 221 is used to open or close the first exhaust port 211. The first lift limiter 230 is connected to the first valve seat 210. The first lift limiter 230 is located on the side of the first valve plate 220 away from the first valve seat 210 to limit the stroke of the first head 221. The second exhaust assembly includes a second valve plate 320 and a second lift limiter 330. The second valve plate 320 includes a second head 321, a second connecting portion 322, and a second fixing portion 323. One end of the second connecting portion 322 is connected to the second head 321, and the other end of the second connecting portion 322 is connected to the second fixing portion 323. The second fixing portion 323 is fixedly connected to the second valve seat 310. The second head 321 is used to open or close the second exhaust port 311. The second lift limiter 330 is connected to the second valve seat 310. The second lift limiter 330 is located on the side of the second valve plate 320 away from the second valve seat 310 to limit the stroke of the second head 321. When the pump body assembly works,The refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber 110 from the suction port of the low-pressure compression chamber 110. The refrigerant completes the first-stage compression in the low-pressure compression chamber 110. Under the action of the gas pressure in the low-pressure compression chamber 110, the first head 221 opens the first exhaust port 211 and the first head 221 abuts against the first lift limiter 230. The refrigerant is discharged through the first exhaust port 211 into the first cavity 121. At this time, the first head 221 closes the first exhaust port 211. The refrigerant in the first cavity 121 is sucked into the high-pressure compression chamber 130 from the suction port of the high-pressure compression chamber 130. The refrigerant completes the second-stage compression in the high-pressure compression chamber 130. Under the action of the gas pressure in the high-pressure compression chamber 130, the second head 321 opens the second exhaust port 311 and the second head 321 abuts against the second lift limiter 330. The refrigerant is discharged through the second exhaust port 311. On the one hand, the low-pressure compression chamber 110 and the high-pressure compression chamber 130 are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. On the other hand, the suction pulsation and exhaust pulsation of the pump body assembly can be effectively reduced, thereby improving the performance of the compressor.

[0047] It should be noted that a first piston 491 is sleeved on the first eccentric part 471, and a second piston 492 is sleeved on the second eccentric part 472. The first piston 491 is rotatably arranged in the low-pressure compression chamber 110, and the second piston 492 is rotatably arranged in the high-pressure compression chamber 130.

[0048] It should be noted that the pump body assembly further includes a lower muffler 460. The lower muffler 460 is connected to the first cylinder 420, and the lower muffler 460 is located on the side of the lower bearing 410 away from the first cylinder 420. The lower muffler 460 and the lower bearing 410 enclose a second cavity 122 of the intermediate cavity 120. The lower bearing 410 is provided with a first valve seat 210, and the first cylinder 420 is provided with a communication channel 123. The two ends of the communication channel 123 are respectively communicated with the first cavity 121 and the second cavity 122. When the pump body assembly works, part of the refrigerant in the low-pressure compression chamber 110 flows into the first cavity 121 from the first exhaust port 211 on the partition assembly 430, and the remaining refrigerant flows into the second cavity 122 from the first exhaust port 211 on the lower bearing 410. The refrigerant in the second cavity 122 flows into the first cavity 121 through the communication channel 123. The refrigerant can be cooled to a certain extent, which is beneficial to reducing the input required for compression in the high-pressure compression chamber 130 and improving the energy efficiency of the compressor.

[0049] As another implementation manner, it may also be that one of the lower bearing 410 and the partition assembly 430 is provided with a first valve seat 210, that is, the low-pressure compression chamber 110 adopts a single-exhaust scheme, which is not limited here.

[0050] Refer to Figures 4 to 7 And in combination with Figure 9 , Figure 4is Figure 3 a partial enlarged view of part B in Figure 5 is Figure 3 a partial enlarged view of part C in Figure 6 is Figure 3 a partial enlarged view of part E in Figure 7 a top view of the first valve plate 220 according to an embodiment of the present invention, Figure 8 a top view of the first valve plate 220 according to another embodiment of the present invention, Figure 9 a top view of the second valve plate 320 according to an embodiment of the present invention. As shown in the figure, in the embodiment of the present invention, the diameter of the first head 221 is D1, the minimum distance between the center of the first head 221 and the connection position where the first fixing portion 223 is connected to the first valve seat 210 is L1, the diameter of the second head 321 is D2, the minimum distance between the center of the second head 321 and the connection position where the second fixing portion 323 is connected to the second valve seat 310 is L2, the working volume of the low-pressure compression chamber 110 is V1, the minimum flow area of the first exhaust port 211 is S1, the working volume of the high-pressure compression chamber 130 is V2, the minimum flow area of the second exhaust port 311 is S2, the lift height of the first lift limiter 230 is H1, the lift height of the second lift limiter 330 is H2, the minimum width of the first connecting portion 222 is F1, the minimum width of the second connecting portion 322 is F2, and it satisfies: U = (V1 × S1 × H1 × L1 × D2 × F2) / (V2 × S2 × H2 × L2 × D1 × F1), 0.37 ≤ U ≤ 8.4. For example, U can be 0.37, 0.5, 1, 1.5, 2, 2.5, 3, 3.5, 4, 4.5, 5, 5.5, 6, 6.5, 7, 7.5, 8, 8.4, etc. It should be noted that the working volume generally refers to the remaining volume between the compression chamber and the piston rotatably installed inside the compression chamber. The unit of the working volume is cc, and the unit of the flow area is mm 2 , and this unit is used in all subsequent embodiments.

[0051] It should be pointed out that a first arc edge Y1 is provided on the side of the first head 221 away from the first fixing portion 223. The diameter of the first head 221 refers to the diameter of the first arc edge Y1, and the center of the first head 221 refers to the center of the first arc edge Y1; a second arc edge Y2 is provided on the side of the second head 321 away from the second fixing portion 323. The diameter of the second head 321 refers to the diameter of the second arc edge Y2, and the center of the second head 321 refers to the center of the second arc edge Y2.

[0052] It should be pointed out that the lift height of the lift limiter refers to the distance between the center of the end face of the exhaust port close to the valve plate and the surface of the lift limiter facing the valve plate on the axis of the exhaust port.

[0053] It should be noted that the minimum width F1 of the first connecting portion 222 refers to the minimum width of the first connecting portion 222 along the direction perpendicular to the first fixing portion 223 to the first head 221, and the minimum width F2 of the second connecting portion 322 refers to the minimum width of the second connecting portion 322 along the direction perpendicular to the second fixing portion 323 to the second head 321.

[0054] It should be noted that when the ratio V2 / V1 of the working volume of the high-pressure compression chamber 130 to the working volume of the low-pressure compression chamber 110 is too small, the working volume V1 of the low-pressure compression chamber 110 is too large, and the high-pressure compression chamber 130 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excessive performance and a decrease in the volumetric efficiency of the compressor; when the ratio V2 / V1 of the working volume of the high-pressure compression chamber 130 to the working volume of the low-pressure compression chamber 110 is too large, for the low-temperature heating condition, the working volume V2 of the high-pressure compression chamber 130 is too large, which is equivalent to the working volume V1 of the low-pressure compression chamber 110 being too small, resulting in insufficient suction volume of the high-pressure compression chamber 130, insufficient heating capacity, and poor user experience.

[0055] It should be noted that if the minimum flow area of the exhaust port is too large, the gas in the compression chamber will be discharged before reaching the designed pressure, resulting in a reduction in the actual exhaust volume of the compression chamber and a decrease in the volumetric efficiency of the compressor; if the minimum flow area of the exhaust port is too small, the gas flow resistance will increase, the gas in the compression chamber cannot be discharged in time, the exhaust pressure will increase, the load of the compressor will increase, resulting in an increase in the power consumption of the compressor and a decrease in the performance of the compressor.

[0056] It should be noted that if the lift height of the lift limiter is too large, the opening angle of the valve plate will be too large. When the opening angle of the valve plate is too large, the flow area at the exhaust port will increase suddenly, the gas flow velocity will decrease, eddy currents or backflows may form, the refrigerant flow resistance will increase, and the exhaust pressure fluctuation will increase, resulting in a decrease in the volumetric efficiency of the compressor; if the lift height of the lift limiter is too small, the opening angle of the valve plate will be too small. When the opening angle of the valve plate is too small, the gas in the compression chamber cannot be discharged in time, the power consumption of the compressor will increase, and the performance of the compressor will decrease.

[0057] It should be noted that if the diameter of the head is too large, the mass of the head will be too large, and the resistance that the valve plate needs to overcome to open will be too large, increasing the exhaust resistance of the compression chamber; if the diameter of the head is too small, the head size of the valve plate will decrease, and the head cannot completely close the exhaust port, and the gas on the high-pressure side is likely to leak back into the compression chamber through the unsealed gap, resulting in a decrease in the exhaust volume of the compressor and a decrease in the performance of the compressor.

[0058] It should be noted that if the minimum width of the connecting part is too large, the rigidity of the valve plate will be too large, the resistance to be overcome for the valve plate to open will be too large, and the exhaust resistance of the compression chamber will increase; if the minimum width of the connecting part is too small, the rigidity of the valve plate will be too small, the gas in the compression chamber will be exhausted before reaching the designed pressure, the actual exhaust volume of the compression chamber will decrease, and the volumetric efficiency of the compressor will decrease.

[0059] It should be noted that if the minimum distance between the center of the head and the connection position of the fixing part and the valve seat is too large, the rigidity of the valve plate will be too small, the gas in the compression chamber will be exhausted before reaching the designed pressure, the actual exhaust volume of the compression chamber will decrease, and the volumetric efficiency of the compressor will decrease; if the minimum distance between the center of the head and the connection position of the fixing part and the valve seat is too small, the rigidity of the valve plate will be too large, the resistance to be overcome for the valve plate to open will be too large, and the exhaust resistance of the compression chamber will increase.

[0060] It can be understood that, on the basis that the working volume V1 of the low-pressure compression chamber 110, the minimum flow-through area S1 of the first exhaust port 211, the lift height H1 of the first lift limiter 230, the minimum width F1 of the first connecting portion 222, the diameter D1 of the first head 221, and the minimum distance L1 between the center of the first head 221 and the connection position where the first fixing portion 223 is connected to the first valve seat 210 remain unchanged, when U is less than 0.37, the working volume V2 of the high-pressure compression chamber 130 is too large, which is equivalent to the working volume V1 of the low-pressure compression chamber 110 being too small. The suction capacity of the high-pressure compression chamber 130 is insufficient, and the heating capacity is insufficient. The flow-through area S2 of the second exhaust port 311 is too large, resulting in the gas in the high-pressure compression chamber 130 being discharged before reaching the designed pressure. The actual exhaust volume of the high-pressure compression chamber 130 decreases, and the volumetric efficiency of the compressor decreases. The lift height H2 of the second lift limiter 330 is too large, resulting in a decrease in gas flow velocity, which may form eddies or backflows, increasing the refrigerant flow resistance. The minimum distance L2 between the center of the second head 321 and the connection position where the second fixing portion 323 is connected to the second valve seat 310 is too large, the diameter D2 of the second head 321 is too small, and the minimum width F2 of the second connecting portion 322 is too small, all of which result in too small rigidity of the valve plate, and the gas in the compression chamber is discharged before reaching the designed pressure, reducing the actual exhaust volume of the compression chamber and the volumetric efficiency of the compressor. Under the combined action of the too large working volume V2 of the high-pressure compression chamber 130, the too large flow-through area S2 of the second exhaust port 311, the too large lift height H2 of the second lift limiter 330, the too large minimum distance L2 between the center of the second head 321 and the connection position where the second fixing portion 323 is connected to the second valve seat 310, the too small diameter D2 of the second head 321, and the too small minimum width F2 of the second connecting portion 322, the actual exhaust volume of the high-pressure compression chamber 130 decreases, and the performance of the compressor deteriorates; when U is greater than 8.At 4 o'clock, the working volume V2 of the high-pressure compression chamber 130 is too small, and the high-pressure compression chamber 130 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in excessive performance, which reduces the volumetric efficiency of the compressor. The flow area S2 of the second exhaust port 311 is too small, resulting in an increase in gas flow resistance. The gas in the high-pressure compression chamber 130 cannot be discharged in time, causing the exhaust pressure to rise and the performance of the compressor to decrease. The lift height H2 of the second lift limiter 330 is too small, resulting in too small an opening angle of the second valve plate 320. The gas in the high-pressure compression chamber 130 cannot be discharged in time, increasing the power consumption of the compressor and reducing the performance of the compressor. The minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310, the too large diameter D2 of the second head 321, and the too large minimum width F2 of the second connecting part 322 all result in too large a rigidity of the valve plate. The resistance that needs to be overcome for the second valve plate 320 to open is too large, increasing the exhaust resistance of the high-pressure compression chamber 130. Under the combined action of the too small working volume V2 of the high-pressure compression chamber 130, the too small flow area S2 of the second exhaust port 311, the too small lift height H2 of the second lift limiter 330, the too small minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310, the too large diameter D2 of the second head 321, and the too large minimum width F2 of the second connecting part 322, the exhaust resistance of the high-pressure compression chamber 130 increases and the performance of the compressor decreases. Therefore, by reasonably designing the relationship between the diameter D1 of the first head 221, the minimum distance L1 between the center of the first head 221 and the connection position where the first fixing part 223 is connected to the first valve seat 210, the diameter D2 of the second head 321, the minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310, the working volume V1 of the low-pressure compression chamber 110, the minimum flow area S1 of the first exhaust port 211, the working volume V2 of the high-pressure compression chamber 130, the minimum flow area S2 of the second exhaust port 311, the lift height H1 of the first lift limiter 230, the lift height H2 of the second lift limiter 330, the minimum width F1 of the first connecting part 222, and the minimum width F2 of the second connecting part 322, the exhaust volume of the high-pressure compression chamber 130 can be increased and the exhaust resistance of the high-pressure compression chamber 130 can be reduced, thereby improving the performance of the compressor.

[0061] Refer to Figure 11 , Figure 11 is the relationship diagram between U and the compressor COP of an embodiment of the present invention. Figure 11 The values in Figure 11The dashed line in [the figure] is the fitting curve of multiple cylinders. As shown in the figure, when the value of U gradually increases, within the range of 0.37 to 8.4, the COP improvement of the compressor first gradually increases and then decreases, and the COP improvement of the compressor is greater than 100%. Therefore, by reasonably designing the relationship between the diameter D1 of the first head 221, the minimum distance L1 between the center of the first head 221 and the connection position where the first fixing part 223 is connected to the first valve seat 210, the diameter D2 of the second head 321, the minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310, the working volume V1 of the low-pressure compression chamber 110, the minimum flow area S1 of the first exhaust port 211, the working volume V2 of the high-pressure compression chamber 130, the minimum flow area S2 of the second exhaust port 311, the lift height H1 of the first lift limiter 230, the lift height H2 of the second lift limiter 330, the minimum width F1 of the first connecting part 222, and the minimum width F2 of the second connecting part 322, the performance of the compressor can be improved. It should be noted that during refrigeration, COP refers to the ratio of the refrigeration capacity of the compressor to the input power; during heating, it is COP during refrigeration + 1. The higher the COP value, the higher the efficiency of the compressor and the more power-saving it is.

[0062] Refer to Figure 7 、 Figure 8 , Figure 8 is a top view of the first valve plate 220 according to another embodiment of the present invention. For example Figure 7 as shown, the first connecting part 222 is a waist-shaped structure, for example Figure 8 as shown, the first connecting part 222 is a fan-shaped structure.

[0063] Refer to Figure 9 、 Figure 10 , Figure 10 is a top view of the second valve plate 320 according to another embodiment of the present invention. For example Figure 9 as shown, the second connecting part 322 is a waist-shaped structure, for example Figure 10 as shown, the second connecting part 322 is a fan-shaped structure.

[0064] For example Figure 4 、 Figure 6 as shown, in the embodiments of the present invention, the lift height H1 of the first lift limiter 230 and the lift height H2 of the second lift limiter 330 satisfy the following specified relationship: H2 ≥ H1, that is, the opening angle of the second valve plate 320 is greater than or equal to the opening angle of the first valve plate 220, which can increase the flow rate at the second exhaust port 311, thereby increasing the exhaust volume of the high-pressure compression chamber 130 to improve the performance of the compressor.

[0065] It can be understood that the exhaust gas flow rate of the high-pressure compression chamber 130 is greater than that of the low-pressure compression chamber 110. When H2 < H1, the opening angle of the second valve plate 320 is smaller than that of the first valve plate 220, and the flow rate of the refrigerant at the second exhaust port 311 is too low, resulting in a reduction in the exhaust gas volume of the high-pressure compression chamber 130 and a decrease in the performance of the compressor. Therefore, by reasonably designing the relationship between the lift height H1 of the first lift limiter 230 and the lift height H2 of the second lift limiter 330, the exhaust gas volume of the high-pressure compression chamber 130 can be increased to improve the performance of the compressor.

[0066] For example Figure 4 、 Figure 6 As shown in, in the embodiment of the present invention, the first limiter includes a first mounting portion 231 and a first limiting portion 232. The first mounting portion 231 has a straight section structure, and the first limiting portion 232 has a curved section structure. The first mounting portion 231 is fixedly connected to the first valve seat 210. One end of the first limiting portion 232 abuts against the first mounting portion 231. When the first head 221 opens the first exhaust port 211, the other end of the first limiting portion 232 abuts against the first head 221. The second limiter includes a second mounting portion 331 and a second limiting portion 332. The second mounting portion 331 has a straight section structure, and the second limiting portion 332 has a curved section structure. The second mounting portion 331 is fixedly connected to the second valve seat 310. One end of the second limiting portion 332 abuts against the second mounting portion 331. When the second head 321 opens the second exhaust port 311, the other end of the second limiting portion 332 abuts against the second head 321. The thickness of the first mounting portion 231 along the axial direction of the crankshaft 470 is T1, and the thickness of the second mounting portion 331 along the axial direction of the crankshaft 470 is T2, satisfying: T2 ≥ T1, so that the second lift limiter 330 can adapt to the second valve plate 320 with stronger impact force, improve the use reliability of the pump body assembly, and thus improve the service life of the compressor.

[0067] It can be understood that the exhaust pressure of the high-pressure compression chamber 130 is greater than that of the low-pressure compression chamber 110, that is, the impact force received by the second valve plate 320 is greater than that received by the first valve plate 220. When the thickness T2 of the second mounting portion 331 along the axial direction of the crankshaft 470 is less than the thickness T1 of the first mounting portion 231 along the axial direction of the crankshaft 470, the stiffness of the second lift limiter 330 is lower than that of the first lift limiter 230. When the compressor operates, the second lift limiter 330 is more likely to produce fatigue fracture, and the service life of the compressor is reduced. Therefore, by reasonably designing the relationship between the thickness T2 of the second mounting portion 331 along the axial direction of the crankshaft 470 and the thickness T1 of the first mounting portion 231 along the axial direction of the crankshaft 470, the use reliability of the pump body assembly can be improved, and thus the service life of the compressor can be improved.

[0068] For example Figure 4 、Figure 6 As shown, in the embodiment of the present invention, the thickness of the first valve plate 220 is T3, and the thickness of the second valve plate 320 is T4, satisfying: 1.3 ≤ T4 / T3 ≤ 1.7. T4 / T3 can be 1.3, 1.4, 1.5, 1.6, 1.7, etc., which can increase the stiffness of the second valve plate 320 and reduce the exhaust resistance of the high-pressure compression chamber 130.

[0069] It can be understood that when T4 / T3 is less than 1.3, the thickness of the second valve plate 320 is too small, that is, the stiffness of the second valve plate 320 is too small. Since the exhaust pressure of the high-pressure compression chamber 130 is greater than the exhaust pressure of the low-pressure compression chamber 110, during the operation of the compressor, the second valve plate 320 is more likely to suffer from fatigue fracture, resulting in a reduction in the service life of the compressor; when T4 / T3 is greater than 1.7, the thickness of the second valve plate 320 is too large, that is, the stiffness of the second valve plate 320 is too large, and the resistance that needs to be overcome for the second valve plate 320 to open is too large, increasing the exhaust resistance of the high-pressure compression chamber 130 and affecting the performance of the compressor. Therefore, by reasonably designing the relationship between the thickness T3 of the first valve plate 220 and the thickness T4 of the second valve plate 320, the stiffness of the second valve plate 320 can be increased and the exhaust resistance of the high-pressure compression chamber 130 can be reduced.

[0070] In the embodiment of the present invention, the thickness of the first valve plate 220 located on the partition assembly 430 is greater than or equal to the thickness of the first valve plate 220 located on the lower bearing 410, that is, the stiffness of the first valve plate 220 located on the partition assembly 430 is greater than the stiffness of the first valve plate 220 located on the lower bearing 410, which can balance the flow rates of the first exhaust ports 211 located on the partition assembly 430 and the first exhaust ports 211 located on the lower bearing 410, so that the exhaust of the low-pressure compression chamber 110 is smooth, the exhaust pulsation of the low-pressure compression chamber 110 can be reduced, and thus the performance of the compressor can be improved.

[0071] It can be understood that the exhaust resistance of the first exhaust port 211 located on the lower bearing 410 is greater than that of the first exhaust port 211 located on the partition assembly 430. When the thickness of the first valve plate 220 located on the partition assembly 430 is less than the thickness of the first valve plate 220 located on the lower bearing 410, the resistance that needs to be overcome for the first valve plate 220 located on the partition assembly 430 to open is less than the resistance that needs to be overcome for the first valve plate 220 located on the lower bearing 410 to open. The opening angle of the first exhaust port 211 located on the partition assembly 430 is much larger than the opening angle of the first exhaust port 211 located on the lower bearing 410, that is, the flow rate of the first exhaust port 211 located on the partition assembly 430 is greater than the flow rate of the opening of the first exhaust port 211 located on the lower bearing 410, resulting in unsmooth exhaust of the low-pressure compression chamber 110 and an increase in the exhaust pulsation of the low-pressure compression chamber 110. Therefore, by reasonably designing the relationship between the thickness of the first valve plate 220 located on the partition assembly 430 and the thickness of the first valve plate 220 located on the lower bearing 410, the exhaust pulsation of the low-pressure compression chamber 110 can be reduced, thereby improving the performance of the compressor.

[0072] In an embodiment of the present invention, the ratio of the working volume of the high-pressure compression chamber 130 to the working volume of the low-pressure compression chamber 110 is V2 / V1, satisfying: 0.4 ≤ V2 / V1 ≤ 0.8. For example, V2 / V1 can be 0.4, 0.5, 0.6, 0.7, 0.8. Taking the working volume of the high-pressure compression chamber 130 remaining unchanged as an example, when V2 / V1 is less than 0.4, the working volume of the low-pressure compression chamber 110 is too large, and the high-pressure compression chamber 130 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in performance surplus and a reduction in the volumetric efficiency of the compressor; when V2 / V1 is greater than 0.8, for the working condition of low-temperature heating, the working volume of the low-pressure compression chamber 110 is too small, the suction volume of the high-pressure compression chamber 130 is too small, and the heating capacity of the compressor decreases, resulting in a poor user experience. Therefore, by reasonably designing the ratio of the working volume of the high-pressure compression chamber 130 to the working volume of the low-pressure compression chamber 110, the suction pulsation and exhaust pulsation can be reduced, the vibration can be reduced, the noise can be lowered, and the volumetric efficiency of the compressor can be improved.

[0073] For example Figure 1 、 Figure 3 As shown, in an embodiment of the present invention, the pump body assembly further includes a lower muffler 460. The lower muffler 460 is connected to the lower bearing 410. The lower bearing 410 and the lower muffler 460 enclose a second cavity 122. The refrigerant in the low-pressure compression chamber 110 sequentially enters the second cavity 122, the communication channel 123, and the first cavity 121, and finally enters the high-pressure compression chamber 130, which is beneficial to reducing the exhaust pulsation and improving the performance of the compressor.

[0074] For example Figure 1As shown, in an embodiment of the present invention, the pump body assembly further includes an upper silencer 480. The upper silencer 480 is connected to the upper bearing 450, and a third cavity 140 is formed between the upper bearing 450 and the upper silencer 480. The exhaust port of the high-pressure compression cavity 130 communicates with the third cavity 140. The refrigerant discharged from the high-pressure compression cavity 130 can enter the third cavity 140 and then be discharged into the inner cavity of the compressor housing, which is beneficial to reducing the exhaust noise and improving the user experience.

[0075] For example Figure 1 、 Figure 3 As shown, in an embodiment of the present invention, the partition assembly 430 includes a first partition 431 and a second partition 432. The first partition 431 and the second partition 432 are arranged opposite to each other along the axial direction of the pump body assembly. The first partition 431 is located below the second partition 432. A first cavity 121 is formed by enclosing between the first partition 431 and the second partition 432. The first partition 431 is connected to the first compression assembly, and the second partition 432 is connected to the second compression assembly. The first partition 431 and the second partition 432 can be processed separately, which is beneficial to machining and manufacturing the second cavity 122 on the partition assembly 430 and can reduce the machining and manufacturing cost of the partition assembly 430.

[0076] For example, the first cavity 121 is a petal-shaped structure and is arranged around the axis O1 of the pump body assembly. By dividing the partition assembly 430 into the first partition 431 and the second partition 432, the first partition 431 and the second partition 432 can be processed separately, which is beneficial to machining and manufacturing the second cavity 122 on the partition assembly 430 and can reduce the machining and manufacturing cost of the partition assembly 430.

[0077] It should be noted that a connection structure is provided between the first partition 431 and the second partition 432, and the connection structure is used to connect and fix the first partition 431 and the second partition 432. For example, the connection structure includes a connecting member, and the connecting member is a screw or a bolt. The connecting member passes through the second partition 432 and is threadedly connected to the first partition 431, which can facilitate the connection and fixation of the first partition 431 and the second partition 432. As another implementation manner, the connecting member is a pin. One end of the connecting member is fixedly connected to the first partition 431, and the other end of the connecting member is fixedly connected to the second partition 432, which can also facilitate the connection and fixation of the first partition 431 and the second partition 432, and will not be elaborated here.

[0078] It should be pointed out that multiple connecting members are provided, and the multiple connecting members are arranged around the axis O1 of the pump body assembly, which can increase the connection stability between the first partition 431 and the second partition 432, and will not be described in detail here.

[0079] Referring to Figure 2 、 Figure 3 , Figure 2Schematic cross-sectional view of a compressor according to an embodiment of the present invention Figure 3 is Figure 2 a cross-sectional view taken along line A-A in the middle. In the embodiment of the present invention, a plurality of communication channels 123 are arranged. The plurality of communication channels 123 are arranged at intervals around the axis O1 of the pump body assembly. Both ends of each communication channel 123 are respectively communicated with the first cavity 121 and the second cavity 122. By arranging the plurality of communication channels 123, the total flow-through area of the plurality of communication channels 123 is increased, the flow rate of the refrigerant can be reduced, and thus the flow loss can be reduced.

[0080] It can be understood that the more the number of the communication channels 123, the lower the strength in the radial direction of the first cylinder 420. In this embodiment, in order to ensure the strength in the radial direction of the first cylinder 420, the number of the communication channels 123 is configured to be less than or equal to 5, for example, the number of the communication channels 123 is 2, 3, 4, 5, etc.

[0081] As another implementation manner, the number of the communication channels 123 can also be configured to be one, which is not limited herein.

[0082] For example Figure 2As shown in the figure, the compressor according to the second aspect embodiment of the present invention includes a housing and the pump body assembly of the above embodiment. The housing has an inner cavity, and the pump body assembly is installed in the inner cavity. By adopting the pump body assembly of the above embodiment, when the pump body assembly works, the refrigerant outside the pump body assembly is sucked into the low-pressure compression chamber 110 from the suction port of the low-pressure compression chamber 110. The refrigerant completes the first-stage compression in the low-pressure compression chamber 110. Under the action of the gas pressure in the low-pressure compression chamber 110, the first head 221 opens the first exhaust port 211 and the first head 221 abuts against the first lift limiter 230. The refrigerant is discharged through the first exhaust port 211 into the first cavity 121. At this time, the first head 221 closes the first exhaust port 211. The refrigerant in the first cavity 121 is sucked into the high-pressure compression chamber 130 from the suction port of the high-pressure compression chamber 130. The refrigerant completes the second-stage compression in the high-pressure compression chamber 130. Under the action of the gas pressure in the high-pressure compression chamber 130, the second head 321 opens the second exhaust port 311 and the second head 321 abuts against the second lift limiter 330. The refrigerant is discharged through the second exhaust port 311. On the one hand, the low-pressure compression chamber 110 and the high-pressure compression chamber 130 are within a reasonable pressure ratio range, which can improve the volumetric efficiency of the compressor. On the other hand, it can effectively reduce the suction pulsation and exhaust pulsation of the pump body assembly, thereby improving the performance of the compressor. The diameter of the first head 221 is D1, the minimum distance between the center of the first head 221 and the connection position where the first fixing portion 223 is connected to the first valve seat 210 is L1, the diameter of the second head 321 is D2, the minimum distance between the center of the second head 321 and the connection position where the second fixing portion 323 is connected to the second valve seat 310 is L2, the working volume of the low-pressure compression chamber 110 is V1, the minimum flow area of the first exhaust port 211 is S1, the working volume of the high-pressure compression chamber 130 is V2, the minimum flow area of the second exhaust port 311 is S2, the lift height of the first lift limiter 230 is H1, the lift height of the second lift limiter 330 is H2, along the direction perpendicular to the first fixing portion 223 to the first head 221, the minimum width of the first connecting portion 222 is F1, along the direction perpendicular to the second fixing portion 323 to the second head 321, the minimum width of the second connecting portion 322 is F2, and it satisfies: U = (V1 × S1 × H1 × L1 × D2 × F2) / (V2 × S2 × H2 × L2 × D1 × F1), 0.37 ≤ U ≤ 8.4. When U is less than 0.When the working volume V2 of the high-pressure compression chamber 130 is too large at 37°C, it is equivalent to that the working volume V1 of the low-pressure compression chamber 110 is too small. The gas intake of the high-pressure compression chamber 130 is insufficient, and the heating capacity is insufficient. The flow area S2 of the second exhaust port 311 is too large, resulting in the gas in the high-pressure compression chamber 130 being discharged before reaching the designed pressure, the actual exhaust volume of the high-pressure compression chamber 130 is reduced, and the volumetric efficiency of the compressor is decreased. The lift height H2 of the second lift limiter 330 is too large, resulting in a decrease in gas flow velocity, which may form eddies or backflows, increasing the refrigerant flow resistance. The minimum distance L2 between the center of the second head 321 and the connection position of the second fixing part 323 to the second valve seat 310 is too large, the diameter D2 of the second head 321 is too small, and the minimum width F2 of the second connecting part 322 is too small, all of which result in too small stiffness of the valve plate, and the gas in the compression chamber is discharged before reaching the designed pressure, the actual exhaust volume of the compression chamber is reduced, and the volumetric efficiency of the compressor is decreased. Under the combined action of the working volume V2 of the high-pressure compression chamber 130 being too large, the flow area S2 of the second exhaust port 311 being too large, the lift height H2 of the second lift limiter 330 being too large, the minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310 being too large, the diameter D2 of the second head 321 being too small, and the minimum width F2 of the second connecting part 322 being too small, the actual exhaust volume of the high-pressure compression chamber 130 is reduced, and the performance of the compressor deteriorates; when U is greater than 8.At 4 o'clock, the working volume V2 of the high-pressure compression chamber 130 is too small, and the high-pressure compression chamber 130 cannot completely consume the refrigerant discharged from the low-pressure compression chamber 110, resulting in performance surplus, which reduces the volumetric efficiency of the compressor. The flow area S2 of the second exhaust port 311 is too small, resulting in an increase in gas flow resistance. The gas in the high-pressure compression chamber 130 cannot be discharged in time, causing the exhaust pressure to rise and the performance of the compressor to decrease. The lift height H2 of the second lift limiter 330 is too small, resulting in too small an opening angle of the second valve plate 320. The gas in the high-pressure compression chamber 130 cannot be discharged in time, increasing the power consumption of the compressor and reducing the performance of the compressor. The minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310 is too small, the diameter D2 of the second head 321 is too large, and the minimum width F2 of the second connecting part 322 is too large, all of which result in too large a rigidity of the valve plate. The resistance that needs to be overcome for the second valve plate 320 to open is too large, increasing the exhaust resistance of the high-pressure compression chamber 130. Under the combined action of the working volume V2 of the high-pressure compression chamber 130 being too small, the flow area S2 of the second exhaust port 311 being too small, the lift height H2 of the second lift limiter 330 being too small, the minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310 being too small, the diameter D2 of the second head 321 being too large, and the minimum width F2 of the second connecting part 322 being too large, the exhaust resistance of the high-pressure compression chamber 130 increases and the performance of the compressor decreases. Therefore, by reasonably designing the relationship between the diameter D1 of the first head 221, the minimum distance L1 between the center of the first head 221 and the connection position where the first fixing part 223 is connected to the first valve seat 210, the diameter D2 of the second head 321, the minimum distance L2 between the center of the second head 321 and the connection position where the second fixing part 323 is connected to the second valve seat 310, the working volume V1 of the low-pressure compression chamber 110, the minimum flow area S1 of the first exhaust port 211, the working volume V2 of the high-pressure compression chamber 130, the minimum flow area S2 of the second exhaust port 311, the lift height H1 of the first lift limiter 230, the lift height H2 of the second lift limiter 330, the minimum width F1 of the first connecting part 222, and the minimum width F2 of the second connecting part 322, the exhaust volume of the high-pressure compression chamber 130 can be increased and the exhaust resistance of the high-pressure compression chamber 130 can be reduced, thereby improving the performance of the compressor.

[0083] In an embodiment of the present invention, the upper bearing 450 of the pump body assembly is fixedly connected to the inner peripheral surface of the inner cavity, or the first cylinder 420 and / or the second cylinder 440 is fixedly connected to the inner peripheral surface of the inner cavity. The fixed connection method can adopt welding or interference fit. Among them, the welding method includes but is not limited to resistance welding and laser welding.

[0084] Since the compressor adopts all the technical solutions of the pump body assembly in the above embodiments, it at least has all the beneficial effects brought by the technical solutions in the above embodiments, which will not be elaborated here.

[0085] The refrigeration device according to the third aspect embodiment of the present invention includes the compressor in the above embodiments. The refrigeration device can be a central air conditioner, an integrated air conditioner, a split air conditioner, an air duct machine, a window air conditioner and other devices.

[0086] The embodiments of the present invention have been described in detail above in conjunction with the accompanying drawings. However, the present invention is not limited to the above embodiments, and various changes can be made without departing from the gist of the present invention within the scope of knowledge possessed by those of ordinary skill in the art.

Claims

1. A pump assembly, characterized in that: A low-pressure compression chamber, an intermediate chamber and a high-pressure compression chamber are provided, wherein the first exhaust port of the low-pressure compression chamber is connected to the air intake port of the high-pressure compression chamber through the intermediate chamber, and the pump body assembly comprises: A first exhaust assembly includes a first valve seat, a first valve plate and a first lift limiter, wherein the first valve seat is provided with the first exhaust port, the first valve plate includes a first head portion, a first connecting portion and a first fixing portion which are connected in sequence, the first head portion is used to open or close the first exhaust port, the first fixing portion and the first lift limiter are both connected to the first valve seat, and the first lift limiter is located on a side of the first valve plate away from the first valve seat; a second exhaust assembly, comprising a second valve seat, a second valve plate and a second lift limiter, wherein the second valve seat is provided with a second exhaust port communicating with the high-pressure compression chamber, the second valve plate comprises a second head portion, a second connecting portion and a second fixing portion connected in sequence, the second head portion is used to open or close the second exhaust port, the second fixing portion and the second lift limiter are both connected to the second valve seat, and the second lift limiter is located on a side of the second valve plate away from the second valve seat; Among them, the working volume of the low-pressure compression chamber is V1, the minimum flow area of ​​the first exhaust port is S1, the working volume of the high-pressure compression chamber is V2, the minimum flow area of ​​the second exhaust port is S2, the lift height of the first lift limiter is H1, the lift height of the second lift limiter is H2, the diameter of the first head is D1, the minimum distance between the center of the first head and the connection position where the first fixing part is connected to the first valve seat is L1, the minimum width of the first connection part is F1, the diameter of the second head is D2, the minimum distance between the center of the second head and the connection position where the second fixing part is connected to the second valve seat is L2, and the minimum width of the second connection part is F2, satisfying: U = (V1×S1×H1×L1×D2×F2) / (V2×S2×H2×L2×D1×F1), 0.37≤U≤8.

4.

2. The pump assembly according to claim 1, characterized in that: A lift height H1 of the first lift limiter is less than or equal to a lift height H2 of the second lift limiter.

3. The pump assembly according to claim 1, characterized in that: The first lift limiter includes a first mounting portion and a first limiting portion connected to the first mounting portion, the first mounting portion is connected to the first valve seat, the first limiting portion is correspondingly arranged to the first head portion to limit the first head portion, the thickness of the first mounting portion along the axial direction of the pump body assembly is T1, the second lift limiter includes a second mounting portion and a second limiting portion connected to the second mounting portion, the second mounting portion is connected to the second valve seat, the second limiting portion is correspondingly arranged to the second head portion to limit the second head portion, the thickness of the second mounting portion along the axial direction of the pump body assembly is T2, satisfying: T2≥T1.

4. The pump assembly according to claim 1, characterized in that: The thickness of the first valve sheet is T3, and the thickness of the second valve sheet is T4, satisfying: 1.3≤T4 / T3≤1.

7.

5. The pump assembly according to claim 1, characterized in that: The ratio of the working volume of the high-pressure compression chamber to the volume of the low-pressure compression chamber is V2 / V1, which satisfies: 0.4≤V2 / V1≤0.

8.

6. The pump assembly according to claim 1, characterized in that: The pump body assembly also includes a lower bearing, a first cylinder, a partition assembly, a second cylinder and an upper bearing connected in sequence, the lower bearing, the first cylinder and the partition assembly enclose the low-pressure compression chamber, the upper bearing, the second cylinder and the partition assembly enclose the high-pressure compression chamber, the partition assembly is provided with a first cavity body of the intermediate cavity, at least one of the partition assembly and the lower bearing is provided with the first valve seat, and the upper bearing is provided with the second valve seat.

7. The pump assembly according to claim 6, characterized in that: The partition assembly and the lower bearing are respectively provided with a first valve seat, and the thickness of the first valve sheet located on the partition assembly is greater than or equal to the thickness of the first valve sheet located on the lower bearing.

8. The pump assembly according to claim 6, characterized in that: The pump body assembly also includes a lower muffler, which is arranged on a side of the lower bearing away from the first cylinder. The lower muffler and the lower bearing enclose a second cavity of the intermediate cavity. The lower bearing is provided with the first valve seat, and the first cylinder is provided with a connecting channel. The two ends of the connecting channel are respectively connected to the first cavity and the second cavity, and the first exhaust port located at the lower bearing exhausts air to the second cavity.

9. The pump assembly according to claim 6, characterized in that: The partition assembly includes a first partition and a second partition that are arranged opposite to each other along the axial direction of the pump body assembly. The first partition and the second partition enclose the first cavity. The first partition is connected to the first cylinder, and the second partition is connected to the second cylinder.

10. A compressor, characterized in that: include: A pump assembly as claimed in any one of claims 1 to 9.

11. Refrigeration equipment, characterized in that: Comprising the compressor as claimed in claim 10.

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