CN102168665A - Cylinder seat of piston type refrigerating compressor - Google Patents
Cylinder seat of piston type refrigerating compressor Download PDFInfo
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- CN102168665A CN102168665A CN2011101126658A CN201110112665A CN102168665A CN 102168665 A CN102168665 A CN 102168665A CN 2011101126658 A CN2011101126658 A CN 2011101126658A CN 201110112665 A CN201110112665 A CN 201110112665A CN 102168665 A CN102168665 A CN 102168665A
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Abstract
The invention discloses a cylinder seat of a piston type refrigerating compressor. A secondary exhaust muffler is arranged and is communicated with a primary exhaust muffler through being connected with a secondary exhaust muffling cavity communicating hole; and an exhaust muffling cover is arranged on the secondary exhaust muffler, is fixed on the secondary exhaust muffler by using a bolt and forms a sealed high pressure gas cavity together with the secondary exhaust muffler. By using the technical scheme, high temperature and high pressure gas flow pulsation and gas flowing speed are reduced and the exhaust noise is reduced because the volume of an exhaust cavity is enlarged; because the secondary muffler has different divergence ratios, the original noise passing through the primary muffler has no muffling frequency and generates acoustic wave reflection in the secondary muffler to increase the sound transmission loss, increase the muffling amount and increase muffling frequencies within different ranges. The secondary muffler largely reduces the gas flow noise together with a Helmholtz gas exhaust resonant cavity; meanwhile, the limit is increased to enhance the operation reliability of a pump body and prolong the service life of the compressor.
Description
Technical field
The invention belongs to the technical field of refrigerating machine, relate to the structure of Piston Refrigerant Compreessor, more particularly, the present invention relates to a kind of cylinder block of Piston Refrigerant Compreessor.
Background technique
The exhaust noise silencing system of existing hermetically sealed compressor constitutes: cylinder head hyperbaric chamber, one-level exhaust noise silencing chamber, interior exhaust coil pipe, and with Helmholtz's exhaust resonant cavity.
Below in conjunction with accompanying drawing prior art constructions and working principle are analyzed:
Fig. 1, Fig. 2 and Fig. 3 are the exhaust noise silencing fluid passage systems of traditional compressor, exhaust noise silencing chamber and Helmholtz's exhaust resonant cavity of expression cylinder-bore, cylinder head assembly, one-level constitute the plan view of fluid passage, and have expressed one-level exhaust noise silencing chamber, Helmholtz's exhaust resonant cavity, the distributing position of cylinder head assembly on cylinder block.
Wherein, represent among the figure: the internal structure in one-level muffler 6 and connection one-level exhaust noise silencing lumen pore road 20 thereof, described one-level muffler 6 is communicated with the cylinder head hyperbaric chamber by connecting one-level exhaust noise silencing lumen pore road 20; Also represented the internal structure in Helmholtz's exhaust resonant cavity 8 and connection Helmholtz exhaust resonant cavity duct 12 thereof, described Helmholtz's exhaust resonant cavity 8 is communicated with the cylinder head hyperbaric chamber by connecting Helmholtz's exhaust resonant cavity duct 12.
The air-flow trend of its refrigerant gas is: from the refrigerant gas of cylinder-bore by the High Temperature High Pressure of valve plate exhaust port discharge, after entering the cylinder head hyperbaric chamber, directly enter the silencing cavity of one-level muffler 6, exhaust coil pipe in entering into is discharged the condenser that compressor enters into refrigeration system at last.
Although the grate flow channel structural system of the compressor of existing band Helmholtz exhaust resonant cavity 8, can significantly reduce the exhaust airstream noise of compressor, but, because Helmholtz's exhaust resonant cavity 8 is single-degree-of-freedom mass-spring systems, very little at accent by gaseous mass, therefore the sound-damping qualities of Helmholtz's exhaust resonant cavity 8 is limited, still can not satisfy the user to low noise requirement.
Simultaneously, because there are many frequencies of passing through in single-stage expanssion type silencing apparatus, always having transmission loss is zero frequency, and promptly the noise of this frequency is not eliminated.
Summary of the invention
Problem to be solved by this invention provides a kind of cylinder block of Piston Refrigerant Compreessor, its objective is the pneumatic noise of reduction from the higher pressure refrigerant gas of compressor discharge.
To achieve these goals, the technological scheme taked of the present invention is:
The cylinder block of Piston Refrigerant Compreessor provided by the present invention, be provided with bent axle, the connecting rod of cylinder, piston and driven plunger, described cylinder block is provided with one-level muffler, Helmholtz's exhaust resonant cavity, and described one-level muffler is communicated with the cylinder head hyperbaric chamber by connecting one-level exhaust noise silencing lumen pore road; Also be provided with the secondary muffler on the described cylinder block, described secondary muffler is communicated with described one-level muffler by connecting secondary exhaust noise silencing chamber intercommunicating pore, establish the exhaust noise silencing lid on the described secondary muffler, described exhaust noise silencing lid on described secondary muffler, and forms the pressurized gas cavity of sealing with the secondary muffler by screw jointly.
Described one-level muffler and secondary muffler are on described cylinder block, with described Helmholtz's exhaust resonant cavity symmetric arrangement.
Described secondary muffler is communicated with interior exhaust coil pipe.
Be communicated with the cross-section area of described one-level muffler and the cross-section area that is connected one-level exhaust noise silencing lumen pore road of cylinder head hyperbaric chamber, described connection secondary exhaust noise silencing chamber intercommunicating pore, be 2mm
2～50mm
2
Described connection one-level exhaust noise silencing lumen pore road is unequal with the cross-section area that is connected secondary exhaust noise silencing chamber intercommunicating pore.
Described secondary muffler and the casting of described cylinder block form an integral body.
The present invention adopts technique scheme, because the exhaust cavity volume enlarges, has reduced high-temperature high-pressure air flow pulsation and gas flow rate, slows down a part of pneumatic noise, has promptly reduced exhaust noise; In addition, because the divergence ratio difference of secondary baffler, originally there is not a noise reduction frequency by the one-level baffler, in the secondary baffler, produce acoustic reflection, increase sound transmission loss, like this, improve sound-damping qualities on the one hand, on the other hand, increase the noise reduction frequency of different range.The secondary baffler cooperates Helmholtz's exhaust resonant cavity, has cut down pneumatic noise greatly, and the operational reliability of the pump housing has been strengthened in simultaneously spacing increase, improves the compressor life-span.
Description of drawings
Below expressed content of each width of cloth accompanying drawing of this specification and the mark among the figure are made brief description:
Fig. 1 is the schematic representation of the exhaust noise silencing fluid passage system of the described traditional compressor of this specification background technique part;
Fig. 2 is the R-R generalized section among Fig. 1;
Fig. 3 is the A-A generalized section among Fig. 1;
Fig. 4 is the schematic representation of compressor air-discharging noise reduction provided by the invention fluid passage system;
Fig. 5 is the full section schematic representation of structure shown in Figure 4;
Fig. 6 is the R-R generalized section among Fig. 4.
Be labeled as among the figure:
1, the stator installation foot, 2, the non-lead end line bag of stator receiving cavity, 3, the cylinder block crankshaft hole, 4, cylinder, 5, the cylinder end face, 6, the one-level muffler, 7, the cylinder head hyperbaric chamber, 8, Helmholtz's exhaust resonant cavity, 12, connect Helmholtz's exhaust resonant cavity duct, 13, valve plate, 14, exhaust port, 15, the cylinder head low-pressure cavity, 16, suction port, 17, piston, 18, suction valve chip, 19, exhaust valve plate, 20, connect one-level exhaust noise silencing lumen pore road, 21, bent axle, 22, connecting rod, 23, the secondary muffler, 24, the exhaust noise silencing lid, 25, screw, 26, connect secondary exhaust noise silencing chamber intercommunicating pore.
Embodiment
Contrast accompanying drawing below, the description by to embodiment is described in further detail the specific embodiment of the present invention, to help those skilled in the art inventive concept of the present invention, technological scheme is had more complete, accurate and deep understanding.
As Fig. 4, Fig. 5 and the expressed structure of the present invention of Fig. 6, be a kind of cylinder block of Piston Refrigerant Compreessor, this compressor is a hermetic piston compressor, is made up of shell, cylinder block, motor, interior exhaust coil pipe etc.Described cylinder block is provided with bent axle 21, the connecting rod 22 of cylinder 4, piston 17 and driven plunger 17, and bent axle 21 is installed in the cylinder block crankshaft hole 3.Described cylinder block is provided with one-level muffler 6, Helmholtz's exhaust resonant cavity 8, and described one-level muffler 6 is communicated with cylinder head hyperbaric chamber 7 by connecting one-level exhaust noise silencing lumen pore road 20.
Described cylinder block comprise be used for installing, the part of supporting motor stator, this part comprises the non-lead end line bag of the stator receiving cavity 2 that is used for holding the non-lead end line bag of stator; Four contour stator installation feet 1 that are used for installing stator lasmination; A part is cylinder block crankshaft hole 3, the cylinder 4 of mounted movable pair.As shown in FIG..A part is the cylinder end face 5 that is used for installing cylinder head assembly; Side at cylinder 4 is provided with Helmholtz's exhaust resonant cavity 8, at the opposite side of cylinder 4 one-level muffler 6 is set.
Cylinder head low-pressure cavity 15 (air intake passage) links by suction port on the valve plate 13 16 and cylinder 4; Cylinder 4 links with cylinder head hyperbaric chamber 7 by the exhaust port 14 on the valve plate 13; One side of cylinder head hyperbaric chamber 7 and Helmholtz's exhaust resonant cavity 8 link, and the silencing cavity of opposite side and one-level muffler 6 links;
The motor (not shown) drives bent axle 21, crankshaft eccentric shaft drivening rod 22, and it is reciprocating in cylinder 4 that connecting rod 22 promotes piston 17.
Piston 17 begins to the lower dead center operation from top dead center, and the gas pressure in the cylinder 4 descends, and when moving to certain distance, exhaust valve plate 19 is closed under the effect of the elastic force of gas pressure difference between cylinder head hyperbaric chamber 7 and the cylinder 4 and exhaust valve plate 19 automatically;
Piston 17 continues operation, gas pressure in the cylinder 4 continues to descend, when reruning to certain distance, gas pressure in the cylinder 4 drops to littler than the interior gas pressure of air intake passage (being cylinder head low-pressure cavity 15), and when its difference is enough to overcome the elastic force of suction valve chip 18, suction valve chip 18 is opened, and gas just enters into the inside of cylinder 4 in the cylinder head low-pressure cavity 15, when piston 17 moves to lower dead center till;
When piston 17 moves to lower dead center, will begin immediately to move to top dead center from lower dead center, gas pressure and temperature in the cylinder 4 will raise; When moving to certain distance, suction valve chip 18 is closed under the effect of the elastic force of gas pressure difference between cylinder 4 and the cylinder head low-pressure cavity 15 and suction valve chip 18 automatically; Piston continues operation, and the gas pressure in the cylinder 4 continues to raise; When reruning to certain distance, gas pressures in the cylinder 4 are elevated to elastic force than gas pressures and exhaust valve plate 19 in the cylinder head hyperbaric chamber 7 big the time, exhaust valve plate 19 is opened, and the refrigerant gas of High Temperature High Pressure just enters in the cylinder head hyperbaric chamber 7 in the cylinder 4.
Then, high-temperature high-pressure refrigerant gas in the cylinder head hyperbaric chamber 7, on the one hand, enter in Helmholtz's exhaust resonant cavity 8 with the Helmholtz's exhaust resonant cavity duct 12 that is connected between the cylinder head hyperbaric chamber 7 along Helmholtz's exhaust resonant cavity 8, with the mixing of pulsing mutually of the gas of its inner High Temperature High Pressure.Because Helmholtz's exhaust resonant cavity is a mass-spring system, the aperture of Helmholtz's exhaust resonant cavity 8 is littler than wave length of sound, the high pressure-temperature gas of certain mass inside reflects, and the acoustic energy that is possessed in the small gaseous mass of accent is absorbed by Helmholtz's exhaust resonant cavity 8 similar pneumatic springs.
When the natural frequency f0 of extraneous incident acoustic wave frequency f and system equated, the air column in the aperture was with regard to producing high vibration owing to resonate, in vibration, and air column and pore-throat sidewall friction and sound energy consumption, thus eliminated a part of low-frequency noise; On the other hand, the high-temperature high-pressure refrigerant gas that comes out in the cylinder head hyperbaric chamber 7 along being connected one-level exhaust noise silencing lumen pore road 20 between cylinder head hyperbaric chamber 7 and the one-level muffler 6, enters into 6 inside, exhaust noise silencing chamber.
In order to solve the problem that exists at the described present known technology of this specification background technique part and to overcome its defective, realize the goal of the invention of reduction from the pneumatic noise of the higher pressure refrigerant gas of compressor discharge, the technological scheme that the present invention takes is:
As shown in Figure 6, also be provided with secondary muffler 23 on the cylinder block of Piston Refrigerant Compreessor provided by the present invention, described secondary muffler 23 is communicated with described one-level muffler 6 by connecting secondary exhaust noise silencing chamber intercommunicating pore 26, establish exhaust noise silencing lid 24 on the described secondary muffler 23, described exhaust noise silencing lid 24 is fixed on the described secondary muffler 23 by screw 25, and with the secondary muffler 23 common pressurized gas cavitys that form sealing.
The structure in expression cylinder head assembly and exhaust noise silencing chamber among the figure, it is the sectional view of cutting open along the axial direction of its gas flow between secondary muffler 23 and the interior exhaust coil pipe, the pressurized gas of having expressed in the cylinder head hyperbaric chamber 7 enter into one-level muffler 6, enter the gas flow of secondary muffler 23 backs to interior exhaust coil pipe by one-level muffler 6 then.
General purpose of the present invention is in the grate flow channel system of compressor, a kind of secondary exhaust muffling device newly is set, be that secondary muffler 23 is the expanssion type silencing apparatus, in former exhaust noise silencing chamber and continuous casting make a secondary silencing cavity, and two silencing cavity are coupled together by processing boring (promptly connecting secondary exhaust noise silencing chamber intercommunicating pore 26), reduce from the pneumatic noise of the higher pressure refrigerant gas of compressor discharge, but this can't make cylinder block structurally more complicated, less because gain in weight, balance to movement does not have influence, increase the spacing of place's pump housing on the contrary, help the reliability of core structure.
The high-temperature high-pressure refrigerant gas that comes out in the cylinder head hyperbaric chamber 7, along being connected one-level exhaust noise silencing lumen pore road 20 between cylinder head hyperbaric chamber 7 and the one-level muffler 6, enter into the inner chamber of one-level muffler 6, again by connecting the inner chamber that secondary exhaust noise silencing chamber intercommunicating pore 26 enters the secondary muffler of setting up 23, exhaust coil pipe in being discharged to then enters the pipeline of refrigeration system.
Above-mentioned solution, on former one-level exhaust muffling device, connect again and increase the exhaust noise silencing channel system of one-level exhaust muffling device, multistage expansion chamber is set, make every grade to have the different frequencies of passing through, and they are together in series, interior exhaust coil pipe is connected second level silencing cavity, utilization secondary noise reduction raising piston reciprocating type refrigeration compressor sound-damping qualities, widen the pneumatic noise noise reduction frequency band of pressure gas refrigerant gas, thereby play the purpose that reduces noise.
As shown in Figure 5, cylinder block and combine with it the longitudinal sectional view of the cylinder head assembly that constitutes the fluid passage, expressed low pressure refrigerant gas and be inhaled into cylinder 4 from cylinder head low-pressure cavity 15, be compressed into higher pressure refrigerant gas then, enter into cylinder head hyperbaric chamber 7, the air-flow by one-level, secondary two-stage silencing cavity moves towards again.
One-level muffler 6 of the present invention and secondary muffler 23 are on described cylinder block, with described Helmholtz's exhaust resonant cavity 8 symmetric arrangement.
As shown in Figure 4, the cylinder block of Piston Refrigerant Compreessor of the present invention and two mufflers thereof, Helmholtz's exhaust resonant cavity 8, constitute the plan view of fluid passage, expressed two-stage exhaust noise silencing chamber, the distributing position of Helmholtz's exhaust resonant cavity 8 on cylinder block.
With exhaust noise silencing chamber and helmholtz resonance chamber symmetric arrangement, interior exhaust coil pipe is connected second level silencing cavity, utilization secondary noise reduction raising piston reciprocating type refrigeration compressor sound-damping qualities is widened the pneumatic noise noise reduction frequency band of pressure gas refrigerant gas, thereby is played the purpose that reduces noise.
The compressor in above-described secondary exhaust noise silencing chamber, the position in compressor air-discharging runner system of its exhaust sympathetic response silencing cavity and air-flow move towards as follows:
One-level muffler 6 links to each other with secondary muffler 23, secondary muffler 23 again with the interior exhaust coil pipe (not shown) that links.After low-temperature low-pressure refrigerant gas entered into cylinder from air intake passage 15 (cylinder head low-pressure cavity), piston 17 was compressed into the refrigerant gas of High Temperature High Pressure with refrigerant gas, and the refrigerant gas of High Temperature High Pressure enters into the hyperbaric chamber 7 of cylinder head then.Pressurized gas in the cylinder head hyperbaric chamber are separated into two parts then, a part enters into Helmholtz's exhaust resonant cavity, another part enters into exhaust noise silencing chamber 6, by hole 22 enter the secondary exhaust disappear chamber 23 link to each other be discharged to then in exhaust coil pipe (not shown) enter into the pipeline of refrigeration system.
Because there is certain divergence ratio newly-designed exhaust noise silencing chamber 23 and exhaust passage, cavity 23 has certain-length simultaneously, after the high-temperature high-pressure refrigerant gas of characteristic frequency of not carrying out noise reduction by the one-level silencing cavity and amplitude enters into ground secondary silencing cavity 23, in the further noise reduction of secondary silencing cavity, can pulse by buffer gas simultaneously, greatly reduce the exhaust noise of compressor.
The secondary exhaust noise silencing chamber 23 that is provided with on the cylinder block, this secondary exhaust noise silencing chamber is connected a pressurized gas cavity that is sealed to form with exhaust noise silencing lid 24 by screw 25.The two-stage baffler of forming connects Helmholtz's exhaust resonant cavity duct 12 by two and communicates with the hyperbaric chamber 7 of 26 cylinder head.
Be communicated with the cross-section area of described one-level muffler 6 and the cross-section area that is connected one-level exhaust noise silencing lumen pore road 20 of cylinder head hyperbaric chamber 7, described connection secondary exhaust noise silencing chamber intercommunicating pore 26, be 2mm
2～50mm
2
Connecting one-level exhaust noise silencing lumen pore road 20 can be circular hole with being connected secondary exhaust noise silencing chamber intercommunicating pore 26, also can be the hole of square hole and other shape, and the cross-section area scope in its duct is 2mm
2～50mm
2
Described connection one-level exhaust noise silencing lumen pore road 20 is unequal with the cross-section area that is connected secondary exhaust noise silencing chamber intercommunicating pore 26.
Obviously adopt the flow passage system of structure of the present invention, the volume of the flow passage structure that the volume of its exhaust receiving cavity is more traditional is big, under the same situation of interior exhaust coil pipe internal diameter cross sectional area and length, the refrigerant gas of High Temperature High Pressure like this, come out from the exhaust receiving cavity, the time that the exhaust coil pipe is consumed in entering will be grown, a part is because the delivery space increase, be that the exhaust cavity volume enlarges, high-temperature high-pressure air flow pulsation and gas flow rate have been reduced, slow down a part of pneumatic noise, can reduce exhaust noise.
The more important thing is, after increasing secondary muffler 23, because the expanssion type silencing apparatus is a secondary muffler 23, it is different that its area and connection secondary exhaust noise silencing chamber intercommunicating pore 26 divergence ratios that connect secondary muffler 23 and original one-level muffler 6 and air-flow path promptly are connected one-level exhaust noise silencing lumen pore road 20 divergence ratios, satisfy kl=n П at some frequency of sound wave, these are by the frequency of the sound wave of one-level muffler 6, can not produce acoustic reflection and reduce transmission loss, but all frequencies are passed through from one-level muffler 6, do not reach and reduce the transmission loss purpose, behind design secondary muffler 23, because the divergence ratio difference of secondary baffler, originally by the one-level baffler do not have a noise reduction frequency, at secondary muffler 23 generation acoustic reflections, increase sound transmission loss, improve sound-damping qualities on the one hand, on the other hand, increase the noise reduction frequency of different range, new design secondary baffler cooperates Helmholtz's exhaust resonant cavity 8, has cut down pneumatic noise greatly.The operational reliability of the pump housing has been strengthened in simultaneously spacing increase, improves the compressor life-span.
In conjunction with the accompanying drawings the present invention has been carried out exemplary description above; obviously specific implementation of the present invention is not subjected to the restriction of aforesaid way; as long as adopted the improvement of the various unsubstantialities that method of the present invention design and technological scheme carry out; or design of the present invention and technological scheme are directly applied to other occasion without improving, all within protection scope of the present invention.
Claims (6)
1. the cylinder block of a Piston Refrigerant Compreessor, be provided with bent axle (21), the connecting rod (22) of cylinder (4), piston (17) and driven plunger (17), described cylinder block is provided with one-level muffler (6), Helmholtz's exhaust resonant cavity (8), and described one-level muffler (6) is communicated with cylinder head hyperbaric chamber (7) by connecting one-level exhaust noise silencing lumen pore road (20); It is characterized in that: also be provided with secondary muffler (23) on the described cylinder block, described secondary muffler (23) is communicated with described one-level muffler (6) by connecting secondary exhaust noise silencing chamber intercommunicating pore (26), establish exhaust noise silencing lid (24) on the described secondary muffler (23), described exhaust noise silencing lid (24) is fixed on the described secondary muffler (23) by screw (25), and forms the pressurized gas cavity that seals jointly with secondary muffler (23).
2. according to the cylinder block of the described Piston Refrigerant Compreessor of claim 1, it is characterized in that: described one-level muffler (6) and secondary muffler (23), on described cylinder block, with described Helmholtz's exhaust resonant cavity (8) symmetric arrangement.
3. according to the cylinder block of the described Piston Refrigerant Compreessor of claim 1, it is characterized in that: described secondary muffler (23) is communicated with interior exhaust coil pipe.
4. according to the cylinder block of the described Piston Refrigerant Compreessor of claim 1, it is characterized in that: be communicated with described one-level muffler (6) and the cross-section area that is connected one-level exhaust noise silencing lumen pore road (20) of cylinder head hyperbaric chamber (7), the cross-section area of described connection secondary exhaust noise silencing chamber intercommunicating pore (26), be 2mm
2～50mm
2
5. according to the cylinder block of the described Piston Refrigerant Compreessor of claim 4, it is characterized in that: described connection one-level exhaust noise silencing lumen pore road (20) is unequal with the cross-section area that is connected secondary exhaust noise silencing chamber intercommunicating pore (26).
6. according to the cylinder block of claim 1 or 2 or 3 or 4 or 5 described Piston Refrigerant Compreessors, it is characterized in that: described secondary muffler (23) forms an integral body with described cylinder block casting.
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| CN2011101126658A CN102168665A (en) | 2011-05-03 | 2011-05-03 | Cylinder seat of piston type refrigerating compressor |
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| Application Number | Priority Date | Filing Date | Title |
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| CN2011101126658A CN102168665A (en) | 2011-05-03 | 2011-05-03 | Cylinder seat of piston type refrigerating compressor |
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| CN2011101126658A Pending CN102168665A (en) | 2011-05-03 | 2011-05-03 | Cylinder seat of piston type refrigerating compressor |
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| CN108980014A (en) * | 2018-09-13 | 2018-12-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Cylinder holder assembly, piston compressor and the refrigeration system of piston compressor |
| CN109441776A (en) * | 2018-12-11 | 2019-03-08 | 芜湖欧宝机电有限公司 | Detachable fission high-efficient compressor cylinder block and its assembly method |
| CN109653994A (en) * | 2018-12-11 | 2019-04-19 | 珠海格力节能环保制冷技术研究中心有限公司 | Head fixing device, compressor and the refrigeration equipment of compressor |
| CN111550387A (en) * | 2020-04-24 | 2020-08-18 | 黄石东贝电器股份有限公司 | Symmetrical cylinder head cylinder block and manufacturing method thereof |
| CN112177887A (en) * | 2020-09-28 | 2021-01-05 | 珠海格力节能环保制冷技术研究中心有限公司 | Exhaust silencing structure and compressor |
| CN113374673A (en) * | 2021-07-08 | 2021-09-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Cylinder block for piston compressor and piston compressor |
| CN114127418A (en) * | 2019-04-29 | 2022-03-01 | 嘉仕达制造股份有限公司 | Silencing device for rocking piston pump and compressor |
| CN114876767A (en) * | 2022-06-08 | 2022-08-09 | 黄石东贝压缩机有限公司 | Muffler and cylinder block |
| CN115342043A (en) * | 2022-07-27 | 2022-11-15 | 珠海格力电器股份有限公司 | Piston compressor and refrigerating device |
| CN116538048A (en) * | 2023-06-30 | 2023-08-04 | 珠海格力电器股份有限公司 | Piston compressor and refrigeration plant |
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| CN108980014A (en) * | 2018-09-13 | 2018-12-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Cylinder holder assembly, piston compressor and the refrigeration system of piston compressor |
| CN108980014B (en) * | 2018-09-13 | 2024-01-30 | 珠海格力节能环保制冷技术研究中心有限公司 | Cylinder block assembly of piston compressor, piston compressor and refrigerating system |
| CN109441776A (en) * | 2018-12-11 | 2019-03-08 | 芜湖欧宝机电有限公司 | Detachable fission high-efficient compressor cylinder block and its assembly method |
| CN109653994A (en) * | 2018-12-11 | 2019-04-19 | 珠海格力节能环保制冷技术研究中心有限公司 | Head fixing device, compressor and the refrigeration equipment of compressor |
| CN114127418A (en) * | 2019-04-29 | 2022-03-01 | 嘉仕达制造股份有限公司 | Silencing device for rocking piston pump and compressor |
| CN114127418B (en) * | 2019-04-29 | 2023-11-21 | 嘉仕达制造股份有限公司 | Silencer for rocking piston pump and compressor |
| CN111550387A (en) * | 2020-04-24 | 2020-08-18 | 黄石东贝电器股份有限公司 | Symmetrical cylinder head cylinder block and manufacturing method thereof |
| CN112177887A (en) * | 2020-09-28 | 2021-01-05 | 珠海格力节能环保制冷技术研究中心有限公司 | Exhaust silencing structure and compressor |
| CN113374673B (en) * | 2021-07-08 | 2022-08-30 | 珠海格力节能环保制冷技术研究中心有限公司 | Cylinder block for piston compressor and piston compressor |
| CN113374673A (en) * | 2021-07-08 | 2021-09-10 | 珠海格力节能环保制冷技术研究中心有限公司 | Cylinder block for piston compressor and piston compressor |
| CN114876767A (en) * | 2022-06-08 | 2022-08-09 | 黄石东贝压缩机有限公司 | Muffler and cylinder block |
| CN115342043A (en) * | 2022-07-27 | 2022-11-15 | 珠海格力电器股份有限公司 | Piston compressor and refrigerating device |
| CN115342043B (en) * | 2022-07-27 | 2024-02-23 | 珠海格力电器股份有限公司 | Piston compressor and refrigerating device |
| CN116538048A (en) * | 2023-06-30 | 2023-08-04 | 珠海格力电器股份有限公司 | Piston compressor and refrigeration plant |
| CN116538048B (en) * | 2023-06-30 | 2023-09-22 | 珠海格力电器股份有限公司 | Piston compressor and refrigeration plant |
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Inventor after: Fang Zeyun Inventor after: Wang Xinnan Inventor after: Cao Lijian Inventor after: He Renshu Inventor after: Zhou Jihui Inventor after: He Jingyun Inventor after: Lin Jun Inventor after: Chen Xi Inventor after: Huang Qiangsheng Inventor before: Fang Zeyun Inventor before: Wang Xinnan Inventor before: He Jingyun Inventor before: Lin Jun Inventor before: Zhao Zhengyang Inventor before: Zou Min Inventor before: Zhou Wei Inventor before: Yang Jingjing |
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Application publication date: 20110831 |