CN221033121U - Pump body assembly, compressor and refrigeration equipment - Google Patents
Pump body assembly, compressor and refrigeration equipment Download PDFInfo
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- CN221033121U CN221033121U CN202322863351.2U CN202322863351U CN221033121U CN 221033121 U CN221033121 U CN 221033121U CN 202322863351 U CN202322863351 U CN 202322863351U CN 221033121 U CN221033121 U CN 221033121U
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- 238000005057 refrigeration Methods 0.000 title claims abstract description 12
- 230000006835 compression Effects 0.000 claims abstract description 104
- 238000007906 compression Methods 0.000 claims abstract description 104
- 238000004891 communication Methods 0.000 claims description 6
- 239000003507 refrigerant Substances 0.000 description 38
- 238000005192 partition Methods 0.000 description 16
- 239000007788 liquid Substances 0.000 description 12
- 238000010438 heat treatment Methods 0.000 description 9
- 230000009471 action Effects 0.000 description 6
- 230000005540 biological transmission Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 6
- 230000033001 locomotion Effects 0.000 description 5
- 230000009286 beneficial effect Effects 0.000 description 4
- 230000001502 supplementing effect Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000005299 abrasion Methods 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002035 prolonged effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 230000003584 silencer Effects 0.000 description 1
- 238000000638 solvent extraction Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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Abstract
The utility model discloses a pump body assembly, a compressor and refrigeration equipment, and relates to the technical field of compressors. The ratio of the contact length of the eccentric part and the piston to the height of the compression cavity is a, and a is more than or equal to 0.28 and less than or equal to 0.9. Limiting a to a range of 0.28 to 0.9 can reduce the friction between the eccentric portion and the piston, thereby reducing the work done by the compressor to overcome the friction during starting and running, and improving the energy efficiency of the compressor.
Description
Technical Field
The utility model relates to the technical field of compressors, in particular to a pump body assembly, a compressor and refrigeration equipment.
Background
In the related art, the compressor comprises a pump body assembly, wherein the pump body assembly is provided with a crankshaft, a piston and a cylinder, and the piston is sleeved on an eccentric part of the crankshaft. The piston is located inside the cylinder and is abutted against the inner wall of the cylinder. When the compressor is stopped for a long time, lubricating oil is concentrated at the bottom of the compressor, that is, the lubricating effect between the eccentric part and the piston is deteriorated, and the energy efficiency of the compressor is lowered because the piston is abutted with the inner wall of the cylinder, which causes the compressor to consume more energy to overcome friction force when the compressor is started.
Disclosure of utility model
The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides a pump body assembly, which reduces the contact length between the eccentric part and the piston, thereby reducing the friction force between the eccentric part and the piston.
The utility model further provides a compressor with the pump body assembly.
According to an embodiment of the first aspect of the utility model, a pump body assembly comprises: at least one cylinder with a compression cavity inside; the crankshaft comprises a main shaft and at least one eccentric part connected with the main shaft, the number of the eccentric parts is equal to that of the cylinders, and the eccentric parts are sleeved with pistons and can be rotatably arranged in the corresponding compression cavities; along the axial direction of the main shaft, the ratio of the contact length of the eccentric part and the piston to the height of the compression cavity is a, and the conditions are satisfied that: a is more than or equal to 0.28 and less than or equal to 0.9.
The pump body assembly provided by the embodiment of the utility model has at least the following beneficial effects:
The piston is sleeved on the eccentric part, and the piston is positioned in the compression cavity of the cylinder, so that the eccentric part drives the piston to make eccentric motion in the cylinder when the crankshaft rotates, and the cylinder is enabled to finish actions such as air suction, compression, air exhaust and the like. The ratio of the contact length of the eccentric part and the piston to the height of the compression cavity is a, and a is more than or equal to 0.28 and less than or equal to 0.9. When a is smaller than 0.28, the contact length of the eccentric part and the piston is shorter, and the piston easily deflects, deforms and misplaces to influence the transmission precision. When a is greater than 0.9, the contact length between the eccentric portion and the piston is long, and it is difficult to achieve the effect of reducing friction. Therefore, the friction force between the eccentric part and the piston can be reduced by limiting a to the range of 0.28 to 0.9, so that the work of the compressor for overcoming the friction force during starting and running is reduced, and the energy efficiency of the compressor can be improved.
According to some embodiments of the utility model, the cylinder is provided with a plurality of cylinders and comprises at least one first cylinder and at least one second cylinder, wherein the first cylinder is internally provided with a low-pressure compression cavity, and the second cylinder is internally provided with a high-pressure compression cavity; the eccentric parts are provided with a plurality of first eccentric parts and at least one second eccentric part, the first eccentric parts are sleeved with first pistons and are rotationally arranged in the corresponding low-pressure compression cavities, and the second eccentric parts are sleeved with second pistons and are rotationally arranged in the corresponding high-pressure compression cavities; and along the axial direction of the main shaft, the contact length of the first eccentric part and the first piston is smaller than or equal to the contact length of the second eccentric part and the second piston.
According to some embodiments of the utility model, the ratio of the span of adjacent first and second eccentric portions to the diameter of the main shaft is b, satisfying: b is more than or equal to 2.5 and less than or equal to 4.5.
According to some embodiments of the utility model, the span of adjacent first and second eccentric portions is H1, the diameter of the first eccentric portion is D1, and the diameter of the second eccentric portion is D2, satisfying: h1/max (D1, D2) is less than or equal to 1.5 and less than or equal to 2.8.
According to some embodiments of the utility model, the pump body assembly is further provided with an intermediate chamber communicating the exhaust port of the low pressure compression chamber with the intake port of the high pressure compression chamber.
According to some embodiments of the utility model, the intermediate chamber comprises a plurality of chambers, the plurality of chambers being communicated by a communication channel, the exhaust port of the low pressure compression chamber being configured to exhaust to one of the chambers or to the plurality of chambers, respectively.
According to some embodiments of the utility model, the pump body assembly is provided with an intermediate chamber, the first cylinders are provided with a plurality of first cylinders, the first cylinders are each provided with the low-pressure compression chamber, and exhaust ports of the plurality of low-pressure compression chambers are communicated with an air inlet of the high-pressure compression chamber through the intermediate chamber.
According to some embodiments of the utility model, the pump body assembly is provided with a middle cavity, the second cylinders are provided with a plurality of high-pressure compression cavities, and air inlets of the high-pressure compression cavities are communicated with the middle cavity.
A compressor according to a second aspect of the present utility model includes the pump body assembly described in the above embodiments.
The compressor provided by the embodiment of the utility model has at least the following beneficial effects:
The pump body assembly is sleeved on the eccentric part through the piston, and the piston is positioned in the compression cavity of the cylinder, so that the piston is driven to do eccentric motion in the cylinder through the eccentric part when the crankshaft rotates, and the cylinder is enabled to finish actions such as air suction, compression, air exhaust and the like. The ratio of the contact length of the eccentric part and the piston to the height of the compression cavity is a, and a is more than or equal to 0.28 and less than or equal to 0.9. When a is smaller than 0.28, the contact length of the eccentric part and the piston is shorter, and the piston easily deflects, deforms and misplaces to influence the transmission precision. When a is greater than 0.9, the contact length between the eccentric portion and the piston is long, and it is difficult to achieve the effect of reducing friction. Therefore, the friction force between the eccentric part and the piston can be reduced by limiting a to the range of 0.28 to 0.9, so that the work of the compressor for overcoming the friction force during starting and running is reduced, and the energy efficiency of the compressor can be improved.
A refrigeration appliance according to a third aspect of the present utility model includes the compressor described in the above embodiment.
The refrigeration equipment provided by the embodiment of the utility model has at least the following beneficial effects:
By adopting the compressor of the embodiment of the second aspect, the pump body component is sleeved on the eccentric part through the piston, and the piston is positioned in the compression cavity of the cylinder, so that the eccentric part drives the piston to make eccentric motion in the cylinder when the crankshaft rotates, and the cylinder can finish actions such as air suction, compression, air exhaust and the like. The ratio of the contact length of the eccentric part and the piston to the height of the compression cavity is a, and a is more than or equal to 0.28 and less than or equal to 0.9. When a is smaller than 0.28, the contact length of the eccentric part and the piston is shorter, and the piston easily deflects, deforms and misplaces to influence the transmission precision. When a is greater than 0.9, the contact length between the eccentric portion and the piston is long, and it is difficult to achieve the effect of reducing friction. Therefore, the friction force between the eccentric part and the piston can be reduced by limiting a to the range of 0.28 to 0.9, so that the work of the compressor for overcoming the friction force during starting and running is reduced, and the energy efficiency of the compressor can be improved.
Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.
Drawings
The utility model is further described with reference to the accompanying drawings and examples, in which:
FIG. 1 is a cross-sectional view of a compressor according to an embodiment of the present utility model;
FIG. 2 is a cross-sectional view of a pump body assembly according to one embodiment of the present utility model;
FIG. 3 is a cross-sectional view of a crankshaft in accordance with one embodiment of the present utility model mated with a first cylinder and a second cylinder;
FIG. 4 is a cross-sectional view of a crankshaft according to one embodiment of the present utility model;
FIG. 5 is a schematic view showing a structure of a compressor according to another embodiment of the present utility model;
FIG. 6 is a sectional view of a compressor according to another embodiment of the present utility model;
fig. 7 is a sectional view of a compressor according to another embodiment of the present utility model.
Reference numerals:
A compressor 1000;
A pump body assembly 100; a first cylinder 110; low pressure compression chamber 111; a lower bearing 120; a lower muffler 130; a first cavity 131; a communication passage 140; an upper bearing 150; a second cylinder 160; a high-pressure compression chamber 161; an upper muffler 170; a third cavity 171; a divider member 190; a second cavity 191; an upper partition 192; a lower partition 193; an intermediate chamber 194;
A housing 200; a lumen 210; an outlet pipe 220;
a reservoir 300; an exhaust pipe 310;
A motor assembly 400; a stator 410; a rotor 420; a crankshaft 430; a first piston 431; a second piston 432; a first eccentric portion 433; a second eccentric portion 434; a main shaft 435;
A first enthalpy increasing assembly 500;
Second enthalpy increasing assembly 600.
Detailed Description
Embodiments of the present utility model are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the utility model.
In the description of the present utility model, it should be understood that the direction or positional relationship indicated with respect to the description of the orientation, such as up, down, etc., is based on the direction or positional relationship shown in the drawings, is merely for convenience of describing the present utility model and simplifying the description, and does not indicate or imply that the apparatus or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as limiting the present utility model.
In the description of the present utility model, plural means two or more. The description of the first and second is for the purpose of distinguishing between technical features only and should not be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated or implicitly indicating the precedence of the technical features indicated.
In the description of the present utility model, unless explicitly defined otherwise, terms such as arrangement, installation, connection, etc. should be construed broadly and the specific meaning of the terms in the present utility model can be reasonably determined by a person skilled in the art in combination with the specific contents of the technical scheme.
The compressor can be used for refrigerating equipment or heating equipment, such as heat pump water heater, air conditioner and the like, and can compress low-temperature and low-pressure refrigerant into high-temperature and high-pressure refrigerant to provide power for the circulation of the refrigerating system. When the compressor finishes the same work load due to the fact that the temperature difference between the temperature of the outdoor heat exchanger and the temperature of the surrounding environment becomes small when the compressor heats in a low-temperature environment or cools in a high-temperature environment, the refrigerating or heating capacity is greatly reduced. Therefore, the compressor can compress the refrigerant in a multistage compression mode, the multistage compression can enable the compressor to have higher volumetric efficiency, the refrigerant pressure discharged by the pump body assembly is improved, and the compressor can achieve a better effect in the low-temperature heating and high-temperature refrigerating occasions.
For example, referring to fig. 1, 2 and 5, a compressor 1000 according to an embodiment of the present utility model includes a housing 200, a pump body assembly 100, a motor assembly 400 and a liquid reservoir 300, wherein the housing 200 has an inner cavity 210, and an air outlet pipe 220 for air outlet is provided at an upper end of the housing 200. The pump body assembly 100 is installed inside the inner cavity 210, and the reservoir 300 is located outside the housing 200 and connected to the pump body assembly 100 through the exhaust pipe 310. The motor assembly 400 includes a stator 410 and a rotor 420, the stator 410 being fixedly coupled to an inner wall of the housing 200, the rotor 420 being positioned between the stators 410.
Referring to fig. 2, the pump body assembly 100 includes a lower bearing 120, a first cylinder 110, a diaphragm member 190, a second cylinder 160, an upper bearing 150, and a crankshaft 430. Wherein the first cylinder 110 and the second cylinder 160 may be one or more, for convenience of explanation, it is explained that each of the first cylinder 110 and the second cylinder 160 is provided with one. The motor assembly 400 is capable of driving the crankshaft 430 to rotate, and the crankshaft 430 includes a first eccentric portion 433 and a second eccentric portion 434 disposed at intervals along an axial direction of the crankshaft 430, wherein the first eccentric portion is sleeved with a first piston 431, and the second eccentric portion is sleeved with a second piston 432. The lower bearing 120 is connected to a lower end surface of the first cylinder 110, the first cylinder 110 is formed with a low pressure compression chamber 111, the first piston 431 is rotatably disposed in the low pressure compression chamber 111, and the reservoir 300 is connected to the first cylinder 110. The partition member 190 is provided on a side of the first cylinder 110 facing away from the lower bearing 120, and the second cylinder 160 is connected to a side of the partition member 190 facing away from the first cylinder 110, the partition member 190 having a function of partitioning the first cylinder 110 and the second cylinder 160. The second cylinder 160 is formed with a high pressure compression chamber 161, and the second piston 432 is rotatably disposed in the high pressure compression chamber 161. The pump body assembly 100 is provided with an intermediate chamber 194, and the exhaust port of the low-pressure compression chamber 111 communicates with the intake port of the high-pressure compression chamber 161 through the intermediate chamber 194. The upper bearing 150 is connected to the upper end surface of the second cylinder 160, and the crankshaft 430 is inserted through the upper bearing 150 and the lower bearing 120, so as to reduce friction force when the crankshaft 430 rotates, and ensure stable operation of the crankshaft 430.
Therefore, when the compressor 1000 is operated, the refrigerant having a low temperature and a low pressure enters the accumulator 300. The liquid reservoir 300 can reduce the liquid refrigerant from entering the pump body assembly 100, so as not to cause liquid impact. The gaseous refrigerant enters the low pressure compression chamber 111 through the discharge pipe 310 of the accumulator 300. When the crankshaft 430 rotates, the first piston 431 is driven to rotate in the low-pressure compression cavity 111, so that the low-temperature low-pressure refrigerant is compressed at one stage, then is discharged to the middle cavity 194 through the exhaust port of the low-pressure compression cavity 111, enters the high-pressure compression cavity 161 through the middle cavity 194 for two-stage compression, finally enters the inner cavity 210 of the shell 200, is further heated by the stator 410 and the rotor 420, becomes the high-temperature high-pressure refrigerant, and is finally discharged from the air outlet pipe 220 of the shell 200. By adopting the two-stage compression mode, the pressure of the refrigerant can be improved, after the initial pressure of the refrigerant after the primary compression is improved to a certain degree, the workload required by the secondary compression is reduced, so that the energy efficiency of the compressor 1000 can be improved, and the compressor 1000 can play a good role in low-temperature heating and high-temperature refrigeration occasions.
To reduce the work done by the compressor 1000 to overcome friction during start-up and operation, referring to FIG. 3, the pump body assembly 100 of the present utility model includes a crankshaft 430 and at least one cylinder having a compression chamber therein. Crankshaft 430 includes a main shaft 435 and at least one eccentric portion, the number of eccentric portions being the same as the number of cylinders. The eccentric part is sleeved with a piston, the piston can rotate relative to the eccentric part, and the eccentric part and the piston are positioned in the compression cavity. When the motor assembly 400 drives the crankshaft 430 to rotate, the crankshaft 430 drives the piston to make eccentric motion in the cylinder through the eccentric portion, so that the cylinder completes actions such as air suction, compression, air exhaust and the like. Because the piston is rotationally connected with the eccentric part, in the working process of the pump body assembly 100, the piston can revolve around the compression cavity and can rotate around the eccentric part, so that the piston is in rolling fit with the wall surface of the compression cavity, friction force can be reduced, abrasion of the piston is relatively uniform, and the service life of the piston is prolonged.
For example, in the embodiment of the present utility model, two cylinders are provided, and the first cylinder 110 and the second cylinder 160 are provided, respectively, the first cylinder 110 is provided with the low pressure compression chamber 111, and the second cylinder 160 is provided with the high pressure compression chamber 161. The piston is provided with two first pistons 431 and second pistons 432 respectively, the crankshaft 430 comprises two eccentric parts, namely a first eccentric part 433 and a second eccentric part 434 respectively, the first eccentric part 433 and the second eccentric part 434 are arranged on the main shaft 435 at intervals, and the first pistons 431 and the second pistons 432 are sleeved on the first eccentric part 433 and the second eccentric part 434 respectively.
Wherein the contact length between the first eccentric portion 433 and the first piston 431 is L 1, and the height of the low-pressure compression chamber 111 is L 2,L1/L2 =a, which satisfies 0.28.ltoreq.a.ltoreq.0.9, for example, a=0.3, a=0.5, a=0.6, a=0.8. When a is smaller than 0.28, the contact length between the first eccentric portion 433 and the first piston 431 is short, and the first piston 431 is liable to deflect, deform and dislocate, which affects the transmission accuracy. When a is greater than 0.9, the contact length between the first eccentric portion 433 and the first piston 431 is long, and it is difficult to reduce friction. Since the height of low-pressure compression chamber 111 is equal or nearly equal to the height of first piston 431, limiting a to the range of 0.28 to 0.9 can reduce the friction force between first eccentric portion 433 and first piston 431, thereby reducing the work done by compressor 1000 to overcome the friction force during starting and operation, and can improve the energy efficiency of compressor 1000.
The contact length between second eccentric portion 434 and second piston 432 is L 3, and the height of high-pressure compression chamber 161 is L 4,L3/L4 =c, satisfying 0.28 c 0.9, for example, c 0.3, c 0.5, c 0.6, and c 0.8. When c is less than 0.28, the contact length between the second eccentric portion 434 and the second piston 432 is short, and the second piston 432 is easily biased, deformed and dislocated, affecting the transmission accuracy. When c is greater than 0.9, the contact length of the second eccentric portion 434 and the second piston 432 is long, and it is difficult to exert an effect of reducing friction. Since the height of the high pressure compression chamber 161 and the height of the second piston 432 are equal or nearly equal, for this reason, limiting a to the range of 0.28 to 0.9 can reduce the friction force between the second eccentric portion 434 and the second piston 432, thereby reducing the work done by the compressor 1000 to overcome the friction force during the starting and operation, and can improve the energy efficiency of the compressor 1000.
In an embodiment of the present utility model, the contact length L 1 of the first eccentric portion 433 and the first piston 431 is less than or equal to the contact length L3 of the second eccentric portion 434 and the second piston 432. It will be appreciated that since the pressure of the refrigerant in the high-pressure compression chamber 161 is high, the pressure applied to the second piston 432 is also high, and it is necessary to secure the second eccentric portion 434 to have a certain strength against deformation. While the refrigerant pressure in low-pressure compression chamber 111 is lower than that in high-pressure compression chamber 161, first eccentric portion 433 requires less strength than second eccentric portion 434. To further reduce friction, L 1 can be designed smaller than L 3. Therefore, by rationally designing the dimensions of L 1 and L 3, it is possible to ensure that the first eccentric portion 433 and the second eccentric portion 434 have proper strength while also reducing friction between the first piston 431 and the first eccentric portion 433, and between the second piston 432 and the second eccentric portion 434.
Referring to fig. 4, in the embodiment of the present utility model, the span of the adjacent first and second eccentric portions 433 and 434 is H 1,H1, which refers to the distance between the end of the first eccentric portion 433 remote from the second eccentric portion 434 and the end of the second eccentric portion 434 remote from the first eccentric portion 433. The diameter of the main shaft 435 is D3, H1/d3=b, satisfying: 2.5.ltoreq.b.ltoreq.4.5, e.g. b=3, b=3.5, b=3.9, b=4. It will be appreciated that assuming b is less than 2.5 and the span between the first and second eccentric portions 433 and 434 is small, there is insufficient space between the first and second eccentric portions 433 and 434 to place the partition member 190, and the partition member 190 is generally provided with the intermediate chamber 194 therein, i.e., it is difficult to perform the function of mixing the refrigerant, which easily results in a reduction in the volume of the intermediate chamber 194, when the diameter of the main shaft 435 is unchanged. Assuming b is greater than 4.5, the span between the first eccentric portion 433 and the second eccentric portion 434 is greater and the strength of the crankshaft 430 is reduced. Therefore, the reasonable design of the size b can ensure that the crankshaft 430 has sufficient strength, and the partition member 190 is arranged in a proper space between the first eccentric portion 433 and the second eccentric portion 434, so that the flexibility of the crankshaft 430 and the volume of the middle chamber 194 are ensured to have proper sizes, the stability and energy efficiency of the compressor 1000 can be improved, and the vibration and noise of the compressor 1000 can be reduced.
With continued reference to FIG. 4, in an embodiment of the present utility model, the diameter of the first eccentric portion 433 is D 1 and the diameter of the second eccentric portion 434 is D 2, satisfying: 1.5.ltoreq.H 1/max(D1,D2). Ltoreq.2.8, it being noted that max (D 1,D2) represents selecting the largest one of D 1 and D 2, for example D 2 is larger than D 1, and 1.5.ltoreq.H 1/D2.ltoreq.2.8; if D 2 is smaller than D 1, 1.5.ltoreq.H 1/D1.ltoreq.2.8. It will be appreciated that the diameters of first eccentric portion 433 and second eccentric portion 434 affect the strength of their connection to main shaft 435, and that the greater the cross-sectional area of first eccentric portion 433 and second eccentric portion 434 connected to main shaft 435, the greater the strength of crankshaft 430. Therefore, when H 1/max(D1,D2) is greater than 2.8, the overall strength of the crankshaft 430 is low, which easily causes bending deformation of the crankshaft 430, and easily causes stress concentration at the connection of the first and second eccentric parts 433 and 434 and the main shaft 435, power consumption increases, and reliability decreases. When H 1/max(D1,D2) is less than 1.5, the strength of the crankshaft 430 is excessively designed, and the weight of the crankshaft 430 is heavy. The power consumption of the compressor 1000 is related to the quality of the crankshaft 430 itself, and design margins may lead to additional power consumption increases, which are detrimental to the performance improvement of the compressor 1000. Therefore, by reasonably designing the relationship between the diameter of the first eccentric portion 433, the diameter of the second eccentric portion 434, and H1, the weight of the crankshaft 430 can be reduced while ensuring a certain strength of the crankshaft 430, power consumption can be reduced, and performance of the compressor 1000 can be improved.
The units of L 1、L2、L3、L4、H1、D1、D2、D3 are all millimeters.
In the embodiment of the present utility model, intermediate chamber 194 includes a plurality of chambers that are communicated through communication passage 140, and the exhaust port of low-pressure compression chamber 111 is configured to exhaust to one of the chambers or to the plurality of chambers, respectively. For example, referring to fig. 2, two of the plurality of cavities are a first cavity 131 and a second cavity 191, respectively. The pump body assembly 100 further includes a lower muffler 130, the lower muffler 130 is connected to the lower bearing 120, a first cavity 131 is formed between the lower muffler 130 and the lower bearing 120, a second cavity 191 is formed in the partition member 190, and the first cavity 131 are communicated through the communication channel 140. Since the displacement of low-pressure compression chamber 111 is generally larger than that of high-pressure compression chamber 161, low-pressure compression chamber 111 may simultaneously discharge gas to first and second chambers 131 and 191 and then mix into high-pressure compression chamber 161 to improve the discharge efficiency. Or in another embodiment, the low-pressure compression chamber 111 may discharge the refrigerant to the first chamber 131 and then enter the second chamber 191 through the communication channel 140, and an appropriate scheme is selected according to practical situations.
With continued reference to FIG. 2, in an embodiment of the utility model, the divider member 190 includes an upper divider 192 and a lower divider 193, with the upper divider 192 being fixedly connected to the lower divider 193. The upper partition 192 is also fixedly connected to the lower end surface of the second cylinder 160, and the lower partition 193 is fixedly connected to the upper end surface of the first cylinder 110. A groove is formed in the side of the upper partition plate 192 facing the lower partition plate 193, and a second cavity 191 is formed by enclosing a wall surface of the groove and a wall surface of the side of the lower partition plate 193 facing the upper partition plate 192. The lower partition 193 is provided with a first valve seat provided with an exhaust port of the low pressure compression chamber 111; the lower bearing 120 is provided with a second valve seat provided with exhaust ports of the low pressure compression chamber 111, that is, two exhaust ports of the low pressure compression chamber 111, and the low pressure compression chamber 111 discharges the refrigerant to the first chamber 131 and the second chamber 191 through the two exhaust ports. Of course, the number of the exhaust ports of the low-pressure compression chamber 111 may be one, three, four, or the like, and an appropriate scheme may be selected according to practical situations.
Referring to fig. 6, in the embodiment of the present utility model, the pump body assembly 100 further includes an upper muffler 170, the upper muffler 170 is connected with the upper bearing 150, and a third cavity 171 is formed between the upper muffler 170 and the upper bearing 150, and the high pressure compression chamber 161 can discharge the compressed refrigerant to the third cavity 171 and finally enter the inner cavity 210 of the housing 200. The upper silencer 170 can reduce noise during refrigerant discharge and improve the use experience of users.
In the embodiment of the present utility model, the low pressure compression chamber 111 is provided in plurality, and the exhaust ports of the plurality of low pressure compression chambers 111 are all communicated with the intermediate chamber 194. For example, a plurality of low-pressure compression chambers 111 are provided in order in the up-down direction. In the embodiment of the present utility model, a plurality of high-pressure compression chambers 161 may be provided, and the air inlets of the plurality of high-pressure compression chambers 161 are all communicated with the intermediate chamber 194, and the plurality of high-pressure compression chambers 161 are sequentially provided in the up-down direction. It is understood that the provision of the plurality of low pressure compression chambers 111 or the plurality of high pressure compression chambers 161 can improve the compression efficiency of the refrigerant.
In order to increase the displacement of the compressor 1000 to increase the capacity of the compressor 1000 for cooling in a high temperature environment or heating in a low temperature environment, referring to fig. 5 and 6, in the embodiment of the present utility model, the compressor 1000 further includes a first enthalpy increasing assembly 500, and the first enthalpy increasing assembly 500 communicates with the intermediate chamber 194. The first enthalpy-increasing component 500 plays a role in supplementing air, can convey the refrigerant into the intermediate chamber 194, and reduces the temperature of the refrigerant by mixing the refrigerant with the original refrigerant in the intermediate chamber 194, thereby reducing the force required by the high-pressure compression chamber 161 for compressing the refrigerant.
Referring to fig. 7, in the embodiment of the present utility model, the compressor 1000 further includes a second enthalpy increasing assembly 600, and the second enthalpy increasing assembly 600 is connected to the low pressure compression chamber 111 through a first passage, thereby delivering a refrigerant into the low pressure compression chamber 111 to increase the discharge amount of the low pressure compression chamber 111. In another embodiment of the present utility model, the second enthalpy-increasing component 600 may be further connected to the high-pressure compression chamber 161, where the second enthalpy-increasing component 600 is used for delivering refrigerant into the high-pressure compression chamber 161 to increase the displacement of the high-pressure compression chamber 161, so as to further increase the capacity of the compressor 1000 for low-temperature heating or high-temperature refrigeration.
In an embodiment of the present utility model, the gaseous refrigerant for supplementing air of the first enthalpy increasing component 500 may be provided through a flash evaporator, which is disposed in a circulation loop of a refrigeration system or a heating system. Taking a heating system as an example: after the liquid refrigerant releases heat through the condenser, the liquid refrigerant flows through the first throttling device, the liquid refrigerant is changed into a refrigerant with mixed gas and liquid under the action of the first throttling device, the refrigerant with mixed gas and liquid enters the flash evaporator, the gaseous refrigerant flows to the first enthalpy-increasing component 500 along the gas outlet of the flash evaporator, the liquid refrigerant flows out from the liquid outlet of the flash evaporator and enters the evaporator after passing through the second throttling device, and finally the refrigerant with absorbed heat enters the low-pressure compression cavity 111 through the liquid reservoir 300. The refrigerant used for supplementing air in the second enthalpy-increasing component 600 may also be provided by flash evaporators, that is, two flash evaporators may be provided in the refrigeration system or the heating system, so as to respectively deliver gaseous refrigerant to the first enthalpy-increasing component 500 and the second enthalpy-increasing component 600. In another embodiment of the present utility model, the flash evaporator may be replaced by a plate heat exchanger, that is, the refrigerant used for supplementing air in the first enthalpy increasing component 500 and the second enthalpy increasing component 600 may also be provided by the plate heat exchanger, and an appropriate scheme is specifically selected according to the actual situation.
The compressor 1000 of one embodiment of the present utility model includes the pump body assembly 100 of the above-described embodiment. The compressor 1000 may be used in refrigeration equipment such as central air conditioners, unitary air conditioners, split air conditioners, ductwork, window winders, and the like. By adopting the pump body assembly 100 of the above embodiment, the piston of the pump body assembly 100 is sleeved on the eccentric portion, and the piston is located in the compression cavity of the cylinder, so that the eccentric portion drives the piston to make eccentric movement in the cylinder when the crankshaft 430 rotates, thereby enabling the cylinder to complete actions such as air suction, compression, air exhaust and the like. The ratio of the contact length of the eccentric part and the piston to the height of the compression cavity is a, and a is more than or equal to 0.28 and less than or equal to 0.9. When a is smaller than 0.28, the contact length of the eccentric part and the piston is shorter, and the piston easily deflects, deforms and misplaces to influence the transmission precision. When a is greater than 0.9, the contact length between the eccentric portion and the piston is long, and it is difficult to achieve the effect of reducing friction. For this reason, limiting a to a range of 0.28 to 0.9 can reduce the friction force between the eccentric portion and the piston, thereby reducing work done by the compressor 1000 to overcome the friction force during starting and operation, and can improve the energy efficiency of the compressor 1000.
Since the compressor 1000 adopts all the technical solutions of the pump body assembly 100 in the above embodiments, at least all the beneficial effects brought by the technical solutions in the above embodiments are provided, and will not be described in detail herein.
The embodiments of the present utility model have been described in detail with reference to the accompanying drawings, but the present utility model is not limited to the above embodiments, and various changes can be made within the knowledge of one of ordinary skill in the art without departing from the spirit of the present utility model.
Claims (10)
1. The pump body subassembly, its characterized in that includes:
at least one cylinder with a compression cavity inside;
The crankshaft comprises a main shaft and at least one eccentric part connected with the main shaft, the number of the eccentric parts is equal to that of the cylinders, and the eccentric parts are sleeved with pistons and can be rotatably arranged in the corresponding compression cavities;
Along the axial direction of the main shaft, the ratio of the contact length of the eccentric part and the piston to the height of the compression cavity is a, and the conditions are satisfied that: a is more than or equal to 0.28 and less than or equal to 0.9.
2. The pump body assembly of claim 1, wherein: the cylinder is provided with a plurality of cylinders and comprises at least one first cylinder and at least one second cylinder, a low-pressure compression cavity is arranged in the first cylinder, and a high-pressure compression cavity is arranged in the second cylinder; the eccentric parts are provided with a plurality of first eccentric parts and at least one second eccentric part, the first eccentric parts are sleeved with first pistons and are rotationally arranged in the corresponding low-pressure compression cavities, and the second eccentric parts are sleeved with second pistons and are rotationally arranged in the corresponding high-pressure compression cavities; and along the axial direction of the main shaft, the contact length of the first eccentric part and the first piston is smaller than or equal to the contact length of the second eccentric part and the second piston.
3. The pump body assembly of claim 2, wherein: the ratio of the span of the adjacent first eccentric portion and second eccentric portion to the diameter of the main shaft is b, satisfying: b is more than or equal to 2.5 and less than or equal to 4.5.
4. The pump body assembly of claim 2, wherein: the span of the adjacent first eccentric part and second eccentric part is H1, the diameter of the first eccentric part is D1, the diameter of the second eccentric part is D2, and the requirements are that: h1/max (D1, D2) is less than or equal to 1.5 and less than or equal to 2.8.
5. The pump body assembly of claim 2, wherein: the pump body assembly is further provided with an intermediate cavity, and the intermediate cavity is communicated with an exhaust port of the low-pressure compression cavity and an air inlet of the high-pressure compression cavity.
6. The pump body assembly of claim 5, wherein: the intermediate chamber includes a plurality of chambers, a plurality of the chambers are communicated through a communication passage, and an exhaust port of the low-pressure compression chamber is configured to exhaust to one of the chambers or to the plurality of chambers, respectively.
7. The pump body assembly of claim 2, wherein: the pump body assembly is provided with a middle cavity, the first cylinders are provided with a plurality of first cylinders, each first cylinder is internally provided with a low-pressure compression cavity, and the exhaust ports of the low-pressure compression cavities are communicated with the air inlets of the high-pressure compression cavities through the middle cavity.
8. The pump body assembly of claim 2, wherein: the pump body assembly is provided with a plurality of middle cavities, each second cylinder is internally provided with a high-pressure compression cavity, and air inlets of the high-pressure compression cavities are communicated with the middle cavities.
9. Compressor, characterized by comprising a pump body assembly according to any one of claims 1 to 8.
10. Refrigeration plant, its characterized in that: comprising the compressor of claim 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322863351.2U CN221033121U (en) | 2023-10-24 | 2023-10-24 | Pump body assembly, compressor and refrigeration equipment |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202322863351.2U CN221033121U (en) | 2023-10-24 | 2023-10-24 | Pump body assembly, compressor and refrigeration equipment |
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| Publication Number | Publication Date |
|---|---|
| CN221033121U true CN221033121U (en) | 2024-05-28 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202322863351.2U Active CN221033121U (en) | 2023-10-24 | 2023-10-24 | Pump body assembly, compressor and refrigeration equipment |
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| Country | Link |
|---|---|
| CN (1) | CN221033121U (en) |
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2023
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