CN215256820U - Pump body subassembly, compressor and air conditioning system - Google Patents
Pump body subassembly, compressor and air conditioning system Download PDFInfo
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- CN215256820U CN215256820U CN202121080550.0U CN202121080550U CN215256820U CN 215256820 U CN215256820 U CN 215256820U CN 202121080550 U CN202121080550 U CN 202121080550U CN 215256820 U CN215256820 U CN 215256820U
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Abstract
The utility model provides a pump body assembly, a compressor and an air conditioning system, wherein the pump body assembly comprises a first flange, a cylinder and a second flange which are sequentially arranged along a first direction, and also comprises a first silencer and a second silencer; the first silencer and the second silencer are communicated through the exhaust flow through hole; a cylinder chamber is arranged in the cylinder, a first flange is provided with a first exhaust hole, the cylinder chamber is communicated with the first silencer through the first exhaust hole, the first flange is provided with a first exhaust valve plate for opening and closing the first exhaust hole, a second flange is provided with a second exhaust hole, the cylinder chamber is communicated with the second silencer through the second exhaust hole, and the second flange is provided with a second exhaust valve plate for opening and closing the second exhaust hole; the first silencer is provided with an exhaust port; the rigidity of the first exhaust valve sheet is greater than that of the second exhaust valve sheet. The pump body assembly can shorten the opening time difference of the upper and lower exhaust valve plates and reduce the pressure loss caused by exhaust pulsation.
Description
Technical Field
The utility model belongs to the technical field of the air conditioning technique and specifically relates to a pump body subassembly, compressor and air conditioning system are related to.
Background
The rolling rotor type compressor has the characteristics of simple structure, low cost, high reliability and the like, and is more and more widely applied to the fields of air conditioners, heat pump water heaters, refrigeration equipment, vehicle-mounted refrigeration systems and the like. In recent years, in order to further improve the energy efficiency of the rolling rotor compressor, a single-cylinder double-row rolling rotor compressor is increasingly adopted. This also presents other problems.
The main function of the compressor in the field of refrigeration systems is to periodically compress refrigerant, so that low-temperature and low-pressure refrigerant is compressed into high-temperature and high-pressure refrigerant to enable the refrigerant to circulate in the refrigeration system. In the periodic compression and exhaust process of the single-cylinder double-row rolling rotor compressor, valve plates in upper and lower flange valve plate seats can continuously open and close exhaust holes, so that the exhaust effect is realized.
Is influenced by the structure of the upper and lower double-exhaust pump body and exhausts downwardsThe air flow needs to flow through the lower silencing cavity and the air cylinder through hole to reach the upper silencing cavity, and the process brings obvious pressure drop to the air flow. Due to the existence of pressure drop, the backpressure values borne by the upper and lower exhaust valve plates are different in the working process of the compressor. The opening condition of the exhaust valve plate is P through analysisIn the cylinder≥PBack pressure+PPrestressing forceWhen the rigidity of the upper and lower exhaust valve plates is the same (namely the pre-acting force of the exhaust valve plates is the same), the opening time of the two exhaust valve plates is inconsistent due to different back pressures and a certain pressure in the cylinder, so that the unfavorable conditions that the upper valve plate is opened firstly and the lower valve plate is opened later are caused, and the pressure loss and the vibration are aggravated due to the exhaust pressure pulsation.
Disclosure of Invention
The utility model discloses a first purpose provides a can shorten about exhaust valve block open time difference, reduce the loss of pressure's that exhaust pulsation brought pump body subassembly.
The second objective of the present invention is to provide a compressor with the above pump body assembly.
A third object of the present invention is to provide an air conditioning system having the above compressor.
In order to achieve the first object, the utility model provides a pump body assembly, which comprises a first flange, a cylinder and a second flange which are arranged in sequence along a first direction; the pump body assembly further comprises a first silencer and a second silencer, and the first silencer and the second silencer are communicated through the exhaust flow through hole; a cylinder chamber is arranged in the cylinder, a first flange is provided with a first exhaust hole, the cylinder chamber is communicated with the first silencer through the first exhaust hole, the first flange is provided with a first exhaust valve plate for opening and closing the first exhaust hole, a second flange is provided with a second exhaust hole, the cylinder chamber is communicated with the second silencer through the second exhaust hole, and the second flange is provided with a second exhaust valve plate for opening and closing the second exhaust hole; the first silencer is provided with an exhaust port; the rigidity of the first exhaust valve sheet is greater than that of the second exhaust valve sheet.
According to the scheme, in the working process of the compressor, the opening time of the exhaust valve plate in the exhaust process of the pump body mainly depends on the back pressure P of the valve plateBack pressurePre-acting force P of low-level and static-state exhaust valve platePrestressing forceSize. When the air pressure P in the cylinderIn the cylinder≥PBack pressure+PPrestressing forceWhen the valve is opened, the valve plate is opened and the exhaust process is performed. And influenced by the double exhaust pump body structure, the air current that the second exhaust hole discharge need flow through second amortization chamber and exhaust circulation hole and just can reach first amortization chamber to discharge from the discharge port in first amortization chamber, because need consider pump body intensity, the aperture of exhaust circulation hole generally can not design great. The exhaust circulation holes with small hole diameters have throttling effect on the airflow, the process can bring obvious pressure drop to the airflow, and the pressure drop effect is more obvious along with the increase of the frequency. The pressure in the second silencing cavity is larger than that in the first silencing cavity due to the action of pressure drop, and the back pressure of the second exhaust valve plate is directly larger than that of the first exhaust valve plate. When the rigidity of the first exhaust valve plate is the same as that of the second exhaust valve plate, the pre-acting force of the first exhaust valve plate is the same as that of the second exhaust valve plate, and P is equal to P in the compression process of the cylinderIn the cylinderAnd the air pressure continuously rises, and the air pressure required by opening the first exhaust valve plate is reached first, and the first exhaust valve plate is opened. With PIn the cylinderAnd continuously rising until the air pressure required for opening the second exhaust valve plate is reached, and then opening the second exhaust valve plate. In the process, the opening time of the first exhaust valve plate is inconsistent with that of the second exhaust valve plate, so that the pressure loss and the vibration are aggravated due to exhaust pressure pulsation.
The utility model discloses a inject the rigidity relation of first exhaust valve piece and second exhaust valve piece, set up the rigidity of the second exhaust valve piece of the higher one side of backpressure into being less than the first exhaust valve piece of the lower one side of backpressure, through suitably reducing second exhaust valve piece rigidity to reduce its PPrestressing forceThe part of the back pressure of the exhaust valve plate is higher than that of the first exhaust valve plate is offset, so that the opening time difference between the first exhaust valve plate and the second exhaust valve plate is shortened, the opening time of the first exhaust valve plate is consistent with or close to that of the second exhaust valve plate, and the pressure loss and the vibration aggravation caused by exhaust pulsation are reduced.
Preferably, the rigidity of the first exhaust valve plate is K1, the rigidity of the second exhaust valve plate is K2, and K1 and K2 satisfy: 0.55K1 < K2 < 0.92K 1.
The further scheme is that the first exhaust valve plate and the second exhaust valve plate are the same in shape and are made of the same material; the thickness of first discharge valve piece is H1, and the thickness of second discharge valve piece is H2, and H1 and H2 satisfy: 0.55H1 < H2 < 0.92H 1.
It can be seen that the rigidity K of the valve sheet is EIHWherein E is the modulus of elasticity, IHThe second moment of area is the waist position equivalent section area moment of inertia. E is only related to the material of the object, therefore, when the material of the exhaust valve plate is fixed, the rigidity of the exhaust valve plate is proportional to the section inertia moment of the equivalent section at the waist position, the section of the exhaust valve plate at the waist position is approximately rectangular, and the section inertia moment in the thickness direction is
When the shapes of the first exhaust valve plate and the second exhaust valve plate are the same, the width L of the waist parts of the first exhaust valve plate and the second exhaust valve plate is equal, so that the rigidity of the valve plates is in direct proportion to the thickness of the valve plates. Therefore, for the exhaust valve plates made of the same material and in the same shape, the rigidity relation of the two exhaust valve plates can be conveniently controlled by only establishing the thickness relation of the two exhaust valve plates.
In a further embodiment, 0.60H1 < H2 < 0.85H 1.
In a further embodiment, 0.65H1 < H2 < 0.75H 1.
Preferably, the thickness H1 of the first exhaust valve plate and the thickness H2 of the second exhaust valve plate are both in the range of 0.1 mm to 0.5 mm.
The first exhaust valve plate and the second exhaust valve plate have the same thickness and the same material; first exhaust valve piece includes first waist, and the width of first waist is L1, and second exhaust valve piece includes the second waist, and the width of second waist is L2, and L1 and L2 satisfy: 0.82L1 < L2 < 0.97L 1.
Therefore, the rigidity of the exhaust valve plate can be adjusted by changing the width or the thickness of the exhaust valve plate.
Further, the width of the first waist portion and the width of the second waist portion are both in the range of 3 mm to 8 mm.
Preferably, the number of the cylinders is one, and the cylinders, the first flange and the second flange define a cylinder chamber.
Therefore, the pump body assembly is a single-cylinder double-row pump body assembly.
The further scheme is that a first flange circulation hole is formed in the first flange, an air cylinder circulation hole is formed in the air cylinder, a second flange circulation hole is formed in the second flange, and the first flange circulation hole, the air cylinder circulation hole and the second flange circulation hole are sequentially connected to form an exhaust circulation hole.
Therefore, after the first exhaust valve plate and the second exhaust valve plate are opened, the airflow flowing through the first exhaust hole enters the first silencing cavity and returns to the refrigerating system from the exhaust hole. The air flow passing through the second exhaust hole enters the second silencing cavity, and then enters the first silencing cavity through the second flange circulation hole, the cylinder circulation hole and the first flange circulation hole in sequence, and then returns to the refrigerating system from the exhaust port.
One preferred scheme is that the number of the cylinders is two, and the two cylinders are respectively a first cylinder and a second cylinder; the pump body assembly further comprises a partition plate, the partition plate is arranged between the first cylinder and the second cylinder, the first flange, the partition plate and the first cylinder enclose a first cylinder chamber, and the second flange, the partition plate and the second cylinder enclose a second cylinder chamber.
Therefore, the pump body assembly is a single-stage pump body assembly with double cylinders and double rows.
The further scheme is that a first flange circulation hole is formed in the first flange, a first cylinder circulation hole is formed in the first cylinder, a partition board circulation hole is formed in the partition board, a second cylinder circulation hole is formed in the second cylinder, a second flange circulation hole is formed in the second flange, and the first flange circulation hole, the first cylinder circulation hole, the partition board circulation hole, the second cylinder circulation hole and the second flange circulation hole are sequentially connected to form an exhaust circulation hole.
Therefore, the air flow passing through the second exhaust hole needs to sequentially pass through the second silencing cavity, the second flange through hole, the second cylinder through hole, the partition plate through hole, the first cylinder through hole and the first flange through hole, enter the first silencing cavity and return to the refrigerating system from the exhaust port.
The first baffle is fixedly connected with the first flange through a first fixing piece, the free end of the first baffle extends towards the first exhaust hole, and a first valve plate swing space is formed between the free end of the first baffle and the first flange.
Therefore, the first baffle is used for limiting the swing amplitude of the first exhaust valve plate.
The second flange is provided with a second baffle, the fixed end of the second baffle and the fixed end of the second exhaust valve plate are fixedly connected with the second flange through a second fixing piece, the free end of the second baffle extends towards the second exhaust hole, and a second valve plate swing space is formed between the free end of the second baffle and the second flange.
Therefore, the second baffle is used for limiting the swing amplitude of the second exhaust valve plate.
One preferred scheme is that the first muffler includes first amortization casing, and first flange includes first valve seat portion and first center pin, and first center pin extends to the direction of keeping away from the cylinder from first valve seat portion along first direction, and first amortization casing cup joints outside first center pin and encloses into first amortization chamber with first valve seat portion, and first exhaust hole is located first valve seat portion.
The second silencer comprises a second silencing shell, the second flange comprises a second valve seat portion and a second central shaft, the second central shaft and the first central shaft are coaxial, the second central shaft extends from the second valve seat portion along the first direction to the direction far away from the cylinder, the second silencing shell and the second valve seat portion enclose a second silencing cavity, and the second exhaust hole is located in the second valve seat portion.
In order to achieve the second objective, the present invention provides a compressor, which comprises the pump body assembly.
To achieve the third objective, the present invention provides an air conditioning system, including the above compressor.
Drawings
Fig. 1 is a sectional view of a first embodiment of the compressor of the present invention.
Fig. 2 is a plan view of the pump body assembly in the first embodiment of the compressor of the present invention.
Fig. 3 is a cross-sectional view at a-a in fig. 2.
Fig. 4 is a partially enlarged view at B in fig. 3.
Fig. 5 is a top view of the first discharge valve plate or the second discharge valve plate in the first embodiment of the compressor of the present invention.
Fig. 6 is a front view of the first or second discharge valve plate in the first embodiment of the compressor of the present invention.
Fig. 7 is a sectional view of a pump body assembly in a second embodiment of the compressor of the present invention.
The present invention will be further explained with reference to the drawings and examples.
Detailed Description
Compressor and first embodiment of pump body assembly thereof
Referring to fig. 1, the compressor includes a compressor body 1 and a liquid distributor 2 connected to each other, the compressor body 1 includes a housing assembly 11, and a pump body assembly 3 and a motor assembly 12, etc. disposed in the housing assembly 11, a crankshaft 121 of the motor assembly 12 extends in a vertical direction, and the pump body assembly 3 is mounted on the crankshaft 121. The pump body assembly 3 in this embodiment is a single-cylinder double-row pump body assembly 3.
Referring to fig. 1 to 3, the pump body assembly 3 includes a first muffler 4, a first flange 5, a cylinder 6, a second flange 7, and a second muffler 8, which are sequentially arranged from top to bottom in a vertical direction. The pump body assembly 3 further includes a roller 122, a vane (not shown), a first discharge valve sheet 91, a second discharge valve sheet 92, a first baffle 93, and a second baffle 94. The cylinder 6 and the first and second flanges 5 and 7 provided at both ends of the cylinder 6 define a cylinder chamber 60, the first and second flanges 5 and 7 axially support a crankshaft 121, an eccentric portion 123 eccentric with respect to a rotation center is provided at a portion of the crankshaft 121 located in the cylinder chamber 60, a roller 122 is fitted to the eccentric portion 123, the roller 122 eccentrically rotates while being in line contact with an inner circumference of the cylinder 6 via an oil film when the crankshaft 121 rotates, and an outer circumference wall of the roller 122 is tightly fitted to a head of a vane so that the cylinder chamber 60 is divided into a suction chamber (low pressure chamber) and a compression chamber (high pressure chamber) by the vane.
The first muffler 4 includes a first muffling housing 41, the first flange 5 includes a first valve seat portion 501 and a first center shaft 502, the first center shaft 502 extends from the first valve seat portion 501 along a vertical direction to a direction away from the cylinder 6, the first muffling housing 41 is sleeved outside the first center shaft 502 and encloses a first muffling chamber 42 with the first valve seat portion 501, and the first valve seat portion 501 is provided with a first exhaust hole 52 and a first flange flow hole 51.
The second muffler 8 includes a second muffler housing 81, the second flange 7 includes a second valve seat portion 701 and a second center shaft 702, the second center shaft 702 is coaxial with the first center shaft 502, the second center shaft 502 extends from the second valve seat portion 701 in a vertical direction in a direction away from the cylinder 6, and the crankshaft 121 of the motor assembly 12 passes through the first center shaft 502 and the second center shaft 702. The second silencing shell 81 and the second valve seat part 701 enclose a second silencing cavity 82, and the second valve seat part 701 is provided with a second exhaust hole 72 and a second flange flow hole 71.
The cylinder 6 is provided with a cylinder circulation hole 61, the first flange circulation hole 51, the cylinder circulation hole 61 and the second flange circulation hole 71 are sequentially connected to form an exhaust flow through hole 31, and the exhaust flow through hole 31 sequentially penetrates through the first flange 5, the cylinder 6 and the second flange 7 along the vertical direction. The first sound-deadening chamber 42 and the second sound-deadening chamber 82 are communicated through the exhaust flow through hole 31, the ratio lambda of the length D of the exhaust flow through hole 31 to the cross-sectional area S of the exhaust flow through hole 31 is in the range of 0.45 to 0.65, and the larger the value of lambda is, the more remarkable the throttling effect of the exhaust flow through hole 31 on the exhaust flow is, and the more remarkable the pressure drop is.
The cylinder chamber 60 and the first muffling chamber 42 are communicated through a first exhaust hole 52, the first flange 5 is provided with a first exhaust valve sheet 91 for opening and closing the first exhaust hole 52, the second flange 7 is provided with a second exhaust hole 72, the cylinder chamber 60 and the second muffling chamber 82 are communicated through the second exhaust hole 72, the second flange 7 is provided with a second exhaust valve sheet 92 for opening and closing the second exhaust hole 72, and the first muffler 4 is provided with an exhaust port (not shown) which is communicated with the first muffling chamber 42 and the refrigeration system.
Referring to fig. 5 and 6, the first exhaust valve sheet 91 includes a head portion 912, a waist portion 913, and a fixing portion 911 connected in this order, the head portion 912 and the fixing portion 911 are respectively connected to both ends of the waist portion 913 in the length direction, and the maximum width of the head portion 912 and the maximum width of the fixing portion 911 are both greater than the width L1 of the waist portion 913. The shape of the second exhaust valve sheet 92 is the same as that of the first exhaust valve sheet 91, and the same shape means the same contour and the same lateral dimension of each part, and only the thickness is different.
The rigidity K1 of the first exhaust valve sheet 91 is greater than the rigidity K2 of the second exhaust valve sheet 92, and K1 and K2 satisfy the following relation: 0.55K1 < K2 < 0.92K 1. The stiffness of the discharge valve plate is typically in the range of 0.05N/mm to 5.26N/mm, and in the prior art compressor, the ratio λ of the length D of the discharge flow hole 31 to the cross-sectional area S of the discharge flow hole 31 is in the range of 0.45 to 0.65. When the ratio lambda is 0.65, the rigidity K2 of the second exhaust valve plate 92 is 0.55 times of the rigidity K1 of the first exhaust valve plate 91, and at the moment, the opening time difference of the two exhaust valve plates of the compressor pump body is the minimum, and the exhaust pressure pulsation is weak. When the ratio λ is 0.45, the stiffness K2 of the second exhaust valve plate 92 is 0.92 times the stiffness K1 of the first exhaust valve plate 91.
In this embodiment, the shape of first exhaust valve piece 91 and second exhaust valve piece 92 is the same and the material is the same, and the thickness of first exhaust valve piece 91 is H1, and the thickness of second exhaust valve piece 92 is H2, therefore, H1 and H2 satisfy: 0.55H1 < H2 < 0.92H 1. Preferably, 0.60H1 < H2 < 0.85H 1. In addition, the thickness H1 of the first exhaust valve sheet 91 and the thickness H2 of the second exhaust valve sheet 92 are both in the range of 0.1 mm to 0.5 mm.
As shown in fig. 3 and 4, the first flange 5 is further provided with a first flap 93, a fixed end 933 of the first flap 93 and a fixed end 911 of the first exhaust valve sheet 91 are both fixedly connected to the first valve seat portion 501 by a first fixing member, a free end 932 of the first flap 93 extends toward the first exhaust hole 52, and a first sheet swing space 931 is formed between the free end 932 of the first flap 93 and the first valve seat portion 501. The second flange 7 is further provided with a second baffle 94, a fixed end of the second baffle 94 and a fixed end of the second exhaust valve plate 92 are both fixedly connected with the second valve seat part 701 through a second fixing member, a free end 942 of the second baffle 94 extends towards the second exhaust hole 72, and a second valve plate swing space 941 is formed between the free end 942 of the second baffle 94 and the second valve seat part 701.
The low-temperature and low-pressure refrigerant from the refrigeration system enters the low-pressure cavity through the suction hole of the cylinder 6, the crankshaft 121 rotates synchronously under the driving of the motor rotor, the roller 122 on the eccentric part 123 of the crankshaft 121 also operates, the low-temperature and low-pressure refrigerant in the low-pressure cavity of the cylinder 6 is compressed gradually under the change of the volume, then the low-temperature and low-pressure refrigerant compressed into the high-temperature and high-pressure refrigerant flows through the first exhaust hole 52 and the second exhaust hole 72 from the upper and lower inclined notches of the high-pressure cavity of the cylinder 6 respectively, and after the first exhaust valve plate 91 and the second exhaust valve plate 92 are opened, the airflow flowing through the first exhaust hole 52 enters the first muffling cavity 42 and returns to the refrigeration system from the exhaust hole. The air flow passing through the second discharge hole 72 enters the second muffling chamber 82, and after sequentially passing through the second flange flow hole 71, the cylinder flow hole 61 and the first flange flow hole 51, enters the first muffling chamber 42, it returns to the refrigeration system from the discharge port, completing the refrigerant compression process of the whole refrigeration cycle.
Therefore, the rigidity of the second exhaust valve plate is smaller than that of the first exhaust valve plate, and the two valve plates have the same pre-deformation amount under the static state, so that the pre-acting force of the second exhaust valve plate is smaller than that of the first exhaust valve plate. The rigidity of the second exhaust valve plate at the side with higher back pressure is set to be smaller than that of the first exhaust valve plate at the side with lower back pressure by limiting the rigidity relation of the first exhaust valve plate and the second exhaust valve plate, and the rigidity of the second exhaust valve plate is properly reduced, so that the P value of the second exhaust valve plate is reducedPrestressing forceThe part of the back pressure of the exhaust valve plate is higher than that of the first exhaust valve plate is offset, so that the opening time difference between the first exhaust valve plate and the second exhaust valve plate is shortened, the opening time of the first exhaust valve plate is consistent with that of the second exhaust valve plate, or the opening time difference between the first exhaust valve plate and the second exhaust valve plate is shortened, and the pressure loss and the vibration aggravation caused by exhaust pulsation are reduced. Experiments prove that when the thickness H1 of the first exhaust valve plate and the thickness H2 of the second exhaust valve plate satisfy the following relational expression: when the pressure pulsation in the air exhaust process of the pump body of the compressor is obviously improved when the pressure pulsation is more than 0.60H1 and less than H2 and less than 0.85H1, the overall energy efficiency of the compressor is improved by about 1%.
In addition, the rigidity of the exhaust valve plate can be changed by changing the width of the exhaust valve plate, for example, the first exhaust valve plate and the second exhaust valve plate are the same in thickness and material; the width of the first waist of first exhaust valve piece is L1, and the width of the second waist of second exhaust valve piece is L2, and L1 and L2 satisfy: 0.82L1 < L2 < 0.97L1, and the width of the first waist portion and the width of the second waist portion are both in the range of 3 mm to 8 mm. Experiments prove that when the first exhaust valve plate and the second exhaust valve plate are the same in thickness and material and the widths L1 and L2 of the waist part meet the relationship, the pressure loss caused by exhaust pressure pulsation can be effectively reduced, and the overall energy efficiency of the compressor is improved by about 0.8%. In other embodiments, the width and thickness of the exhaust valve plate can be adjusted at the same time to adjust the rigidity of the exhaust valve plate.
Compressor and pump body assembly second embodiment thereof
As a description of the second embodiment of the compressor and the pump body assembly of the present invention, only the differences from the first embodiment of the compressor and the pump body assembly will be described below.
Referring to fig. 7, the pump body assembly 23 in this embodiment is a double cylinder, double row, single stage pump body assembly. The number of cylinders is two, and the two cylinders are a first cylinder 261 and a second cylinder 262, respectively. The pump body assembly 23 further includes a partition 232, the partition 232 is disposed between the first cylinder 261 and the second cylinder 262, the first flange 25, the partition 232 and the first cylinder 261 define a first cylinder chamber 2611, and the second flange 27, the partition 232 and the second cylinder 262 define a second cylinder chamber 2621.
The first flange 25 is provided with a first flange circulation hole 251, the first cylinder 261 is provided with a first cylinder circulation hole 2612, the partition plate 232 is provided with a partition plate circulation hole 2321, the second cylinder 262 is provided with a second cylinder circulation hole 2622, and the second flange 27 is provided with a second flange circulation hole 271. The first flange circulation hole 251, the first cylinder circulation hole 2612, the diaphragm circulation hole 2321, the second cylinder circulation hole 2622 and the second flange circulation hole 271 are connected in this order to form the exhaust flow passage 231.
After the second exhaust valve plate 292 is opened, the air flowing through the second exhaust hole 272 needs to flow through the second muffling chamber 282, the second flange circulation hole 271, the second cylinder circulation hole 2622, the partition plate circulation hole 2321, the first cylinder circulation hole 2612 and the first flange circulation hole 251 in sequence, enter the first muffling chamber 242 and return to the refrigeration system from the exhaust port.
The lower exhaust gas flow also has a pressure drop effect when flowing through the exhaust gas flow hole 231, so that the problem of pressure pulsation caused by inconsistent opening timings of the first exhaust valve plate 291 and the second exhaust valve plate 292 can be alleviated by defining the rigidity relationship between the first exhaust valve plate 291 and the second exhaust valve plate 292 and setting the rigidity of the second exhaust valve plate 292 to be smaller than that of the first exhaust valve plate 291. In addition, because the distance of the whole exhaust flow through hole 231 in the system with the double-cylinder double-row single-stage pump body assembly is longer than that of a single-cylinder double-row system, the pressure drop effect of the air flow in the whole circulation process is more obvious, and the difference of the back pressures of the first exhaust valve plate 291 and the second exhaust valve plate 292 is larger. The exhaust pressure pulsation and the vibration caused by the exhaust pulsation are more severe in the pump body exhaust process.
In this embodiment, the first exhaust valve plate 291 and the second exhaust valve plate 292 are the same in shape and material, and H1 and H2 satisfy the following relation: 0.60H1 < H2 < 0.85H 1. Preferably, 0.65H1 < H2 < 0.75H 1. At this time, when H1 and H2 satisfy the above relationship, the stiffness of the second exhaust valve plate 292 is smaller than that of the first exhaust valve plate 291, and the two exhaust valve plates have the same amount of pre-deformation in a static state, so the pre-acting force of the second exhaust valve plate 292 will be smaller than that of the first exhaust valve plate 291. The part of the second exhaust valve plate 292 with the back pressure higher than the first exhaust valve plate 291 can be just offset by the part of the second exhaust valve plate with the back pressure lower than the pre-acting force of the first exhaust valve plate 291, so that the opening time of the two exhaust valve plates is consistent or the opening time difference of the two exhaust valve plates is shortened, and the pressure pulsation in the exhaust process of the compressor pump body is reduced. Experiments prove that when the thickness H1 of the first exhaust valve plate 291 and the thickness H2 of the second exhaust valve plate 292 satisfy the following relational expression: when the pressure pulsation in the air exhaust process of the pump body of the compressor is more than 0.65H1 and less than H2 and less than 0.75H1, the overall energy efficiency of the compressor is improved by about 1.5%.
Air conditioning system embodiment
The air conditioning system of the present embodiment includes the compressor in each of the compressor embodiments described above.
In addition, for the horizontal type compressor, the first muffler, the first flange, the cylinder, the second flange, and the second muffler may also be sequentially arranged in the horizontal direction. The first silencer and the second silencer can also be connected by a pipeline, and the exhaust flow through hole is positioned on the pipeline. The above changes also enable the object of the present invention to be achieved.
Finally, it should be emphasized that the above-described preferred embodiments of the present invention are merely examples of implementations, and are not intended to limit the scope of the present invention, as those skilled in the art will appreciate that various changes and modifications may be made without departing from the spirit and scope of the invention, and it is intended to cover all such modifications, equivalents, and improvements as fall within the true spirit and scope of the invention.
Claims (18)
1. The pump body assembly comprises a first flange, a cylinder and a second flange which are sequentially arranged along a first direction, and further comprises a first silencer and a second silencer, wherein the first silencer and the second silencer are communicated through an exhaust flow through hole;
a cylinder chamber is arranged in the cylinder, a first exhaust hole is formed in the first flange, the cylinder chamber is communicated with the first silencer through the first exhaust hole, and the first flange is provided with a first exhaust valve plate for opening and closing the first exhaust hole;
the second flange is provided with a second exhaust hole, the cylinder chamber is communicated with the second muffler through the second exhaust hole, and the second flange is provided with a second exhaust valve plate for opening and closing the second exhaust hole;
the first silencer is provided with an exhaust port;
the method is characterized in that:
the rigidity of the first exhaust valve plate is larger than that of the second exhaust valve plate.
2. The pump body assembly of claim 1, wherein:
the rigidity of the first exhaust valve plate is K1, the rigidity of the second exhaust valve plate is K2, and K1 and K2 meet the following requirements: 0.55K1 < K2 < 0.92K 1.
3. The pump body assembly of claim 2, wherein:
the first exhaust valve plate and the second exhaust valve plate are the same in shape and material;
the thickness of first discharge valve piece is H1, the thickness of second discharge valve piece is H2, and H1 and H2 satisfy: 0.55H1 < H2 < 0.92H 1.
4. The pump body assembly of claim 3, wherein:
0.60H1＜H2＜0.85H1。
5. the pump body assembly of claim 4, wherein:
0.65H1＜H2＜0.75H1。
6. the pump body assembly according to any one of claims 3 to 5, wherein:
the thickness H1 of the first exhaust valve plate and the thickness H2 of the second exhaust valve plate are both in the range of 0.1 mm to 0.5 mm.
7. The pump body assembly of claim 2, wherein:
the first exhaust valve plate and the second exhaust valve plate are the same in thickness and material;
first exhaust valve piece includes first waist, the width of first waist is L1, second exhaust valve piece includes the second waist, the width of second waist is L2, and L1 and L2 satisfy: 0.82L1 < L2 < 0.97L 1.
8. The pump body assembly of claim 7, wherein:
the width of the first waist portion and the width of the second waist portion are both in the range of 3 mm to 8 mm.
9. The pump body assembly according to any one of claims 1 to 5, wherein:
the number of the air cylinders is one, and the cylinder chamber is defined by the air cylinders, the first flange and the second flange.
10. The pump body assembly of claim 9, wherein:
the first flange is provided with a first flange circulation hole, the cylinder is provided with a cylinder circulation hole, the second flange is provided with a second flange circulation hole, and the first flange circulation hole, the cylinder circulation hole and the second flange circulation hole are sequentially connected to form the exhaust circulation hole.
11. The pump body assembly according to any one of claims 1 to 5, wherein:
the number of the cylinders is two, and the two cylinders are respectively a first cylinder and a second cylinder;
the pump body assembly further comprises a partition plate, the partition plate is arranged between the first cylinder and the second cylinder, a first cylinder chamber is defined by the first flange, the partition plate and the first cylinder, and a second cylinder chamber is defined by the second flange, the partition plate and the second cylinder.
12. The pump body assembly of claim 11, wherein:
the first flange is provided with a first flange circulation hole, the first cylinder is provided with a first cylinder circulation hole, the partition plate is provided with a partition plate circulation hole, the second cylinder is provided with a second cylinder circulation hole, and the second flange is provided with a second flange circulation hole;
the first flange circulation hole, the first cylinder circulation hole, the partition plate circulation hole, the second cylinder circulation hole, and the second flange circulation hole are connected in sequence to form the exhaust gas circulation hole.
13. The pump body assembly according to any one of claims 1 to 5, wherein:
the first flange is further provided with a first baffle, the fixed end of the first baffle and the fixed end of the first exhaust valve block are fixedly connected with the first flange through a first fixing piece, the free end of the first baffle faces towards the first exhaust hole, and a first valve block swing space is formed between the free end of the first baffle and the first flange.
14. The pump body assembly according to any one of claims 1 to 5, wherein:
the second flange is further provided with a second baffle, the fixed end of the second baffle and the fixed end of the second exhaust valve plate are fixedly connected with the second flange through a second fixing piece, the free end of the second baffle faces the second exhaust hole and extends, and a second valve plate swing space is formed between the free end of the second baffle and the second flange.
15. The pump body assembly according to any one of claims 1 to 5, wherein:
the first muffler includes first amortization casing, first flange includes first valve seat portion and first center pin, first center pin certainly first valve seat portion is followed first direction is to keeping away from the direction of cylinder extends, first amortization casing cup joints outside the first center pin and with first valve seat portion encloses into first amortization chamber, first exhaust hole is located on the first valve seat portion.
16. The pump body assembly of claim 15, wherein:
the second muffler includes a second muffler shell, the second flange includes a second valve seat portion and a second center shaft, the second center shaft is coaxial with the first center shaft, the second center shaft extends from the second valve seat portion along the first direction to a direction away from the cylinder, the second muffler shell and the second valve seat portion enclose a second muffler chamber, and the second exhaust hole is located on the second valve seat portion.
17. A compressor, comprising a pump body assembly according to any one of claims 1 to 16.
18. An air conditioning system comprising the compressor of claim 17.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121080550.0U CN215256820U (en) | 2021-05-19 | 2021-05-19 | Pump body subassembly, compressor and air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121080550.0U CN215256820U (en) | 2021-05-19 | 2021-05-19 | Pump body subassembly, compressor and air conditioning system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN215256820U true CN215256820U (en) | 2021-12-21 |
Family
ID=79457534
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202121080550.0U Active CN215256820U (en) | 2021-05-19 | 2021-05-19 | Pump body subassembly, compressor and air conditioning system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN215256820U (en) |
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2021
- 2021-05-19 CN CN202121080550.0U patent/CN215256820U/en active Active
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