阅读说明：本技术 一种泵体结构、压缩机和空调器 (Pump body structure, compressor and air conditioner ) 是由 张心爱 王珺 吴健 闫鹏举 张大鹏 黄纯浚 于 2021-09-14 设计创作，主要内容包括：本公开提供一种泵体结构、压缩机和空调器,泵体结构包括：第一气缸、第二气缸和隔板,所述第二气缸位于所述第一气缸的下方,所述隔板位于所述第一气缸和所述第二气缸之间,所述第一气缸上开设有第一排气流通通道,所述第二气缸上设置有第二排气流通通道,所述隔板上设置有中间腔,所述第二气缸的排气能够依次经过所述第二排气流通通道、所述中间腔和所述第一排气流通通道,所述中间腔的流通面积比所述第二排气流通通道大,所述中间腔的流通面积也比所述第一排气流通通道大。根据本公开能够使得第二气缸在其排气流路上形成扩张型的消声结构,减缓双缸压缩机下排气流路气流脉动及气动噪声,提高压缩机用户听感体验。(The utility model provides a pump body structure, compressor and air conditioner, pump body structure includes: first cylinder, second cylinder and baffle, the second cylinder is located the below of first cylinder, the baffle is located first cylinder with between the second cylinder, first exhaust circulation passageway has been seted up on the first cylinder, be provided with second exhaust circulation passageway on the second cylinder, be provided with middle chamber on the baffle, the exhaust of second cylinder can pass through in proper order second exhaust circulation passageway middle chamber with first exhaust circulation passageway, the flow area ratio of middle chamber second exhaust circulation passageway is big, the flow area of middle chamber also compares first exhaust circulation passageway is big. According to the double-cylinder compressor exhaust silencer, the second cylinder can form an expansion type silencing structure on the exhaust flow path of the second cylinder, the airflow pulsation and the pneumatic noise of the exhaust flow path of the double-cylinder compressor are reduced, and the auditory experience of a compressor user is improved.)

1. A pump body structure, its characterized in that: the method comprises the following steps:

a first cylinder (5), a second cylinder (7) and a partition plate (6), the second cylinder (7) being located below the first cylinder (5), the partition (6) is located between the first cylinder (5) and the second cylinder (7), a first exhaust circulation channel (112) is arranged on the first cylinder (5), a second exhaust circulation channel (111) is arranged on the second cylinder (7), an intermediate cavity (100) is arranged on the partition plate (6), the exhaust gas of the second cylinder (7) can sequentially pass through the second exhaust gas circulation channel (111), the intermediate cavity (100) and the first exhaust gas circulation channel (112), the flow area of the intermediate chamber (100) is larger than the second exhaust gas flow passage (111), the flow area of the intermediate chamber (100) is also larger than the first exhaust gas flow passage (112).

2. The pump body structure according to claim 1, wherein:

still include first flange (2) and first muffler (3), first flange (2) set up in on the terminal surface of a side of first cylinder (5) with second cylinder (7) back of the body mutually, first muffler (3) lid is established on the terminal surface of a side of first flange (2) with first cylinder (5) back of the body mutually, first muffler (3) with form first amortization chamber (31) between first flange (2), be provided with first exhaust hole on first flange (2), the exhaust process of first cylinder (5) first exhaust hole gets into in first amortization chamber (31).

3. The pump body structure according to claim 2, wherein:

the muffler is characterized by further comprising a second flange (9) and a second muffler (10), wherein the second flange (9) is arranged on one side end face, back to the first cylinder (5), of the second cylinder (7), the second muffler (10) is covered on one side end face, back to the second cylinder (7), of the second flange (9), a second silencing cavity (101) is formed between the second muffler (10) and the second flange (9), a second exhaust hole is formed in the second flange (9), and exhaust of the second cylinder (7) enters the second silencing cavity (101) through the second exhaust hole;

a second communicating hole (91) is further formed in the second flange (9), one end of the second communicating hole (91) is communicated with the second silencing cavity (101), and the other end of the second communicating hole is communicated to a second exhaust circulation channel (111) of the second cylinder (7);

the first flange (2) is further provided with a first communicating hole (21), one end of the first communicating hole (21) is communicated with the first silencing cavity (31), and the other end of the first communicating hole is communicated to the first exhaust circulation channel (112) of the first cylinder (5).

4. The pump body structure according to any one of claims 1 to 3, wherein:

the baffle plate (6) comprises a first baffle plate (61) and a second baffle plate (62), a first cavity (200) is formed inside the first baffle plate (61), a second cavity (300) is formed inside the second baffle plate (62), one axial side of the first baffle plate (61) is connected with the first cylinder (5), one axial side of the second baffle plate (62) is connected with the second cylinder (7), and the other axial side of the first baffle plate (61) is connected with the other axial side of the second baffle plate (62), so that the first cavity (200) is opposite to the second cavity (300) and is spliced to form the middle cavity (100).

5. The pump body structure according to claim 4, wherein:

the first partition board (61) is also provided with a first circulation outlet (611), one end of the first circulation outlet (611) is communicated with the first cavity (200), and the other end of the first circulation outlet is communicated with the first exhaust circulation channel (112); the cross-sectional area of the first flow-through outlet (611) decreases or is constant from the junction with the first cavity (200) to the junction with the first exhaust gas flow-through channel (112); and/or the presence of a gas in the gas,

the second partition plate (62) is also provided with a first circulation inlet (621), one end of the first circulation inlet (621) is communicated with the second cavity (300), and the other end of the first circulation inlet is communicated with the second exhaust circulation channel (111); the cross-sectional area of the first circulation outlet (611) is gradually reduced or constant from the junction with the second cavity (300) to the junction with the second exhaust circulation passage (111).

6. The pump body structure according to claim 5, wherein:

the first cavity (200) is an annular sinking cavity, and the second cavity (300) is an annular sinking cavity; and/or the longitudinal cross-sectional shape of the first circulation outlet (611) is trapezoidal or rectangular, and the longitudinal cross-sectional shape of the first circulation inlet (621) is trapezoidal or rectangular.

7. The pump body structure according to claim 4, wherein:

setting the inner diameter of the middle cavity as D1, and the inner diameter of the first cylinder or the second cylinder as D, the parameters D1 and D need to satisfy: d1 > D.

8. The pump body structure according to any one of claims 1 to 7, wherein:

the partition plate (6) comprises a third partition plate (63), a third cavity (400) is formed in the third partition plate (63), one axial side of the third partition plate (63) is connected with the first cylinder (5), the other axial side of the third partition plate is connected with the second cylinder (7), and the third cavity (400) forms the middle cavity (100).

9. The pump body structure according to claim 8, wherein:

a second circulation outlet (631) is further formed in the third partition plate (63), one end of the second circulation outlet (631) is communicated with the third cavity (400), and the other end of the second circulation outlet is communicated with the first exhaust circulation channel (112); the cross-sectional area of the second flow outlet (631) decreases or does not change from the junction with the third cavity (400) to the junction with the first exhaust gas flow channel (112);

or, a second circulation inlet (632) is further arranged on the third partition plate (63), one end of the second circulation inlet (632) is communicated with the third cavity (400), and the other end is communicated with the second exhaust circulation channel (111); the cross-sectional area of the second flow-through inlet (632) decreases or does not change from the junction with the third cavity (400) to the junction with the second exhaust gas flow-through passage (111).

10. The pump body structure according to claim 8, wherein:

one end of the third cavity (400) is communicated with the first exhaust gas circulation channel (112), and the other end is communicated with the second exhaust gas circulation channel (111);

the novel corrugated partition board is characterized by further comprising at least two reinforcing ribs (64), wherein the at least two reinforcing ribs (64) are arranged in the third cavity (400) and are arranged along the circumferential direction of the third partition board (63) at intervals, and the third cavity (400) is divided into a plurality of small cavities along the circumferential direction.

11. The pump body structure according to claim 10, wherein:

setting the thickness of the reinforcing rib along the axial direction to be H, the inner diameter of the third cavity (400) to be D2, the axial height of the third partition plate (63) to be H, the inner diameter of the first cylinder or the second cylinder to be D, and meeting the following parameters of H, H, D2 and D: h is less than H, D2 is more than D.

12. The pump body structure according to claim 11, wherein:

the parameters H, H, D2 and D need to satisfy: h is more than 2 and less than H-5, and D2 is more than D + 5.

13. A compressor, characterized by: comprising a pump body structure according to any one of claims 1-12.

14. An air conditioner, characterized in that: comprising the compressor of claim 13.

Technical Field

The disclosure relates to the technical field of compressors, in particular to a pump body structure, a compressor and an air conditioner.

Background

The conventional rolling rotor type double-cylinder compressor pump body component consists of a crankshaft, an upper silencer, an upper roller, an upper air cylinder, a partition plate, a lower air cylinder, a lower roller, an upper flange component, a lower flange component (comprising an upper flange, a lower flange, an exhaust valve plate and a valve plate limit baffle), a lower silencer and a sliding sheet And (5) exhausting. The pulsation of the air flow generated by the periodic suction and discharge processes of the compressor is one of the main sources of the pneumatic noise of the rotor compressor. The exhaust circulation channel is an axial hole which runs through the lower flange and the upper flange, due to the limitation of a design space, the flow area is relatively small generally, particularly, the trend of the development of the miniaturization and high-speed of the compressor is gradually shown in recent years, the noise experience feeling can be ensured when the compressor is in series design, the series design is required to be reduced, the design space of the exhaust circulation channel and the flow area of the lower exhaust flow are further limited, the compressor operates at high frequency, particularly, under the heavy working condition, the gas flow speed is high, the pneumatic noise is more serious, the overall noise of the compressor is greatly increased, and the exhaust circulation channel becomes one of difficult problems which need to be solved urgently in the research and development process of the existing small high-frequency compressor product.

Because the double-cylinder compressor among the prior art has when descending a series design because size compression leads to the exhaust flow path air current pulsation increase of lower cylinder, the pneumatic noise of compressor complete machine increase, compressor user's listening experience subalternation technical problem, consequently this disclosure research designs a pump body structure, compressor and air conditioner.

BRIEF SUMMARY OF THE PRESENT DISCLOSURE

Therefore, the technical problem to be solved by the present disclosure is to overcome the defects that when a two-cylinder or multi-cylinder compressor in the prior art is designed to be reduced in series, the pulsation of the air flow of the exhaust flow path of the lower cylinder is increased due to the size compression, the pneumatic noise of the whole compressor is increased, and the listening experience of the compressor user is poor, so as to provide a pump body structure, a compressor and an air conditioner.

In order to solve the above problem, the present disclosure provides a pump body structure, which includes:

first cylinder, second cylinder and baffle, the second cylinder is located the below of first cylinder, the baffle is located first cylinder with between the second cylinder, first exhaust circulation passageway has been seted up on the first cylinder, be provided with second exhaust circulation passageway on the second cylinder, be provided with middle chamber on the baffle, the exhaust of second cylinder can pass through in proper order second exhaust circulation passageway middle chamber with first exhaust circulation passageway, the flow area ratio of middle chamber second exhaust circulation passageway is big, the flow area of middle chamber also compares first exhaust circulation passageway is big.

In some embodiments, the muffler further includes a first flange and a first muffler, the first flange is disposed on a side end surface of the first cylinder opposite to the second cylinder, the first muffler cover is disposed on a side end surface of the first flange opposite to the first cylinder, a first muffling chamber is formed between the first muffler and the first flange, a first exhaust hole is disposed on the first flange, and exhaust gas of the first cylinder enters the first muffling chamber through the first exhaust hole.

In some embodiments, the muffler further comprises a second flange and a second muffler, the second flange is disposed on a side end surface of the second cylinder opposite to the first cylinder, the second muffler cover is disposed on a side end surface of the second flange opposite to the second cylinder, a second muffling cavity is formed between the second muffler and the second flange, a second exhaust hole is disposed on the second flange, and exhaust gas of the second cylinder enters the second muffling cavity through the second exhaust hole;

the second flange is also provided with a second communicating hole, one end of the second communicating hole is communicated with the second silencing cavity, and the other end of the second communicating hole is communicated to the second exhaust circulation channel of the second cylinder;

the first flange is further provided with a first communicating hole, one end of the first communicating hole is communicated with the first silencing cavity, and the other end of the first communicating hole is communicated to the first exhaust circulation channel of the first air cylinder.

In some embodiments, the partition plate includes a first partition plate and a second partition plate, the first partition plate has a first cavity formed therein, the second partition plate has a second cavity formed therein, one axial side of the first partition plate is connected to the first cylinder, one axial side of the second partition plate is connected to the second cylinder, and the other axial side of the first partition plate is connected to the other axial side of the second partition plate, such that the first cavity is opposite to the second cavity and is spliced to form the intermediate cavity.

In some embodiments, the first partition plate is further provided with a first circulation outlet, one end of the first circulation outlet is communicated with the first cavity, and the other end of the first circulation outlet is communicated with the first exhaust circulation channel; the cross-sectional area of the first circulation outlet is gradually reduced or unchanged from the joint of the first cavity to the joint of the first exhaust circulation passage;

the second partition plate is also provided with a first flow inlet, one end of the first flow inlet is communicated with the second cavity, and the other end of the first flow inlet is communicated with the second exhaust flow channel; the cross-sectional area of the first flow-through outlet decreases or does not change from the point of connection with the second cavity to the point of connection with the second exhaust gas flow-through passage.

In some embodiments, the first cavity is an annular counterbore and the second cavity is an annular counterbore; and/or the longitudinal section of the first circulation inlet is trapezoidal or rectangular, and the longitudinal section of the first circulation outlet is trapezoidal or rectangular.

In some embodiments, if the inner diameter of the middle cavity is D1 and the inner diameter of the first cylinder or the second cylinder is D, the parameters D1 and D should satisfy: d1 > D.

In some embodiments, the partition includes a third partition having a third cavity formed therein, the third partition being connected to the first cylinder on one axial side and to the second cylinder on the other axial side, the third cavity forming the intermediate chamber.

In some embodiments, a second flow outlet is further disposed on the third partition, and one end of the second flow outlet is communicated with the third cavity, and the other end of the second flow outlet is communicated with the first exhaust gas flow channel; the cross-sectional area of the second circulation outlet is gradually reduced or unchanged from the joint of the second circulation outlet and the third cavity to the joint of the second circulation outlet and the first exhaust circulation passage;

or, a second flow inlet is further formed in the third partition plate, one end of the second flow inlet is communicated with the third cavity, and the other end of the second flow inlet is communicated with the second exhaust flow channel; the cross-sectional area of the second flow inlet decreases or does not change from the junction with the third cavity to the junction with the second exhaust gas flow passage.

In some embodiments, one end of the third cavity is in communication with the first exhaust gas flow passage and the other end is in communication with the second exhaust gas flow passage;

still include two at least strengthening ribs, two at least the strengthening rib set up in the third cavity and follow the circumference direction interval arrangement of third baffle will a plurality of little cavitys are separated into along the circumference direction to the third cavity.

In some embodiments, the thickness of the reinforcing rib along the axial direction is set to be H, the inner diameter of the first cavity is set to be D2, the axial height of the third partition board is set to be H, the inner diameter of the first cylinder or the second cylinder is set to be D, and the parameters H, D2 and D are required to satisfy: h is less than H, D2 is more than D.

In some embodiments, the parameters H, D2, D are such that: h is more than 2 and less than H-5, and D2 is more than D + 5.

The present disclosure also provides a compressor including the pump body structure of any one of the foregoing.

The present disclosure also provides an air conditioner including the compressor of any one of the preceding claims.

The pump body structure, the compressor and the air conditioner have the following beneficial effects:

the utility model discloses a through the middle chamber structure of seting up on the baffle between first cylinder and second cylinder, can make the exhaust of second cylinder get into the middle chamber through the second exhaust circulation passageway on the second cylinder, reentry in the first exhaust circulation passageway, and the flow area of middle chamber is greater than first exhaust circulation passageway, also be greater than second exhaust circulation passageway, can make the second cylinder form the noise cancelling structure of expanding type on its exhaust flow path, the expanding type cavity communicates between second exhaust circulation passageway and first exhaust circulation passageway, the sound wave is inside its expanding cavity reflection, refraction when the air current circulation passes through the expanding cavity, so as to consume the energy, thereby reach the purpose that reduces the noise, thereby effectively slow down exhaust flow path air pulsation and pneumatic noise under the compressor, greatly reduce compressor complete machine noise, improve compressor user's listening sense experience, the problem of double-cylinder or multi-cylinder compressor because the size compression leads to the exhaust flow path air current pulsation increase of lower cylinder when descending series design, the pneumatic noise of compressor complete machine increases, and compressor user listening experience is poor is solved.

Drawings

FIG. 1 is a longitudinal internal cross-sectional view of a compressor pump body structure of the present disclosure;

FIG. 1a is a partial enlarged view of portion A of FIG. 1;

FIG. 1b is a cross-sectional view of the separator of FIG. 1;

FIG. 1c is an exploded view of the separator of FIG. 1;

FIG. 1d is a cross-sectional view of the separator of FIG. 1 after detonation;

FIG. 2 is a longitudinal cross-sectional view of a compressor pump body structure according to an alternative first embodiment of the present disclosure;

FIG. 2a is an enlarged structural view of the separator in FIG. 2;

FIG. 3 is a longitudinal cross-sectional view of a compressor pump body structure according to an alternative second embodiment of the present disclosure;

FIG. 3a is an enlarged structural view of the partition in FIG. 3;

FIG. 4 is a longitudinal cross-sectional view of a compressor pump body structure according to a third alternative embodiment of the present disclosure;

FIG. 4a is an enlarged structural view of the separator in FIG. 4;

FIG. 5 is a longitudinal cross-sectional view of a compressor pump body structure according to an alternative fourth embodiment of the present disclosure;

FIG. 5a is an enlarged structural view of the first separator in FIG. 5;

fig. 5b is an enlarged structural view of the second separator in fig. 5.

The reference numerals are represented as:

1. a crankshaft; 2. a first flange; 21. a first communication hole; 3. a first muffler; 4. a first roller; 5. a first cylinder; 6. a partition plate; 61. a first separator; 611. a first flow-through outlet; 612. a first open end face; 613. a first non-open end face; 62. a second separator; 621. a first flow-through inlet; 622. a second open end face; 623. a second non-open end face; 63. a third partition plate; 631. a second flow-through outlet; 632. a second flow-through inlet; 64. reinforcing ribs; 7. a second cylinder; 8. a second roller; 9. a second flange; 91. a second communication hole; 10. a second muffler; 31. a first muffling chamber; 101. a second muffling chamber; 100. a middle cavity; 200. a first cavity; 300. a second cavity; 400. a third cavity; 112. a first exhaust gas flow passage; 111. a second exhaust gas flow passage.

Detailed Description

As shown in fig. 1-5b, the present disclosure provides a pump body structure comprising:

first cylinder 5, second cylinder 7 and baffle 6, second cylinder 7 is located the below of first cylinder 5, baffle 6 is located first cylinder 5 with between the second cylinder 7, first exhaust circulation passageway 112 has been seted up on the first cylinder 5, be provided with second exhaust circulation passageway 111 on the second cylinder 7, be provided with middle chamber 100 (third amortization chamber promptly) on the baffle 6, the exhaust of second cylinder 7 can pass through in proper order second exhaust circulation passageway 111 middle chamber 100 with first exhaust circulation passageway 112, the flow area ratio of middle chamber 100 second exhaust circulation passageway 111 is big, the flow area ratio of middle chamber 100 is also bigger than first exhaust circulation passageway 112.

The utility model discloses a through the middle chamber structure of seting up on the baffle between first cylinder and second cylinder, can make the exhaust of second cylinder get into the middle chamber through the second exhaust circulation passageway on the second cylinder, reentry in the first exhaust circulation passageway, and the flow area of middle chamber is greater than first exhaust circulation passageway, also be greater than second exhaust circulation passageway, can make the second cylinder form the noise cancelling structure of expanding type on its exhaust flow path, the expanding type cavity communicates between second exhaust circulation passageway and first exhaust circulation passageway, the sound wave is inside its expanding cavity reflection, refraction when the air current circulation passes through the expanding cavity, so as to consume the energy, thereby reach the purpose that reduces the noise, thereby effectively slow down exhaust flow path air pulsation and pneumatic noise under the compressor, greatly reduce compressor complete machine noise, improve compressor user's listening sense experience, the problem of double-cylinder or multi-cylinder compressor because the size compression leads to the exhaust flow path air current pulsation increase of lower cylinder when descending series design, the pneumatic noise of compressor complete machine increases, and compressor user listening experience is poor is solved.

The double-cylinder rotor compressor, especially the small-sized high-frequency compressor, has small flow area due to the space design limitation of the lower cylinder flow passage, and the compressor operates at high frequency, especially under heavy working conditions, when the gas discharged from the lower cylinder flows through the exhaust flow passage, the gas flow speed is high, and serious pneumatic noise is generated, so that the noise of the whole compressor is greatly increased.

The utility model discloses focus to the big problem of pneumatic noise that the aforesaid arouses because of small-size high frequency compressor exhaust circulation passageway design limitation, provide a compressor with double-cylinder pump body subassembly structure, through optimizing exhaust passage, the expanding amortization runner of innovative design on exhaust circulation passageway effectively improves the air current pulsation of double-cylinder compressor pump body exhaust circulation passageway, the pneumatic noise of exhaust when greatly reduced compressor high frequency operation to a great extent improves compressor complete machine pneumatic noise.

In some embodiments, the cylinder muffler further includes a first flange 2 and a first muffler 3, the first flange 2 is disposed on a side end surface of the first cylinder 5 opposite to the second cylinder 7, the first muffler 3 is disposed on a side end surface of the first flange 2 opposite to the first cylinder 5, a first muffling chamber 31 is formed between the first muffler 3 and the first flange 2, a first exhaust hole is disposed on the first flange 2, and exhaust gas of the first cylinder 5 enters the first muffling chamber 31 through the first exhaust hole. This is the preferred structural style of this disclosure, can fix the first cylinder through first flange, forms first amortization chamber between first muffler and the first flange, can play the effect of amortization to the exhaust of first cylinder.

In some embodiments, the cylinder muffler further comprises a second flange 9 and a second muffler 10, the second flange 9 is disposed on a side end surface of the second cylinder 7 opposite to the first cylinder 5, the second muffler 10 covers a side end surface of the second flange 9 opposite to the second cylinder 7, a second muffling chamber 101 is formed between the second muffler 10 and the second flange 9, a second exhaust hole is disposed on the second flange 9, and exhaust gas of the second cylinder 7 enters the second muffling chamber 101 through the second exhaust hole;

the second flange 9 is further provided with a second communication hole 91, one end of the second communication hole 91 is communicated with the second silencing cavity 101, and the other end of the second communication hole 91 is communicated with the second exhaust circulation channel 111 of the second cylinder 7;

the first flange 2 is further provided with a first communication hole 21, one end of the first communication hole 21 is communicated with the first silencing cavity 31, and the other end is communicated with the first exhaust gas circulation passage 112 of the first cylinder 5.

The second cylinder can be fixed through the second flange, the second muffler and the second flange form a second silencing cavity, so that the airflow from the second cylinder is subjected to first-stage silencing, the gas in the first silencing cavity enters a second exhaust circulation channel of the second cylinder through a second communication hole in the second flange and then enters a middle cavity of the partition plate, an expanding silencing effect is performed at the position, and the gas is exhausted through the first exhaust circulation channel after silencing, enters the first silencing cavity and is mixed with the exhaust of the first cylinder; the exhaust of the lower cylinder (second cylinder) is subjected to expanding silencing through the middle cavity (third silencing cavity) of the partition plate, and the problem of pneumatic noise increase caused by shortening of the exhaust path of the second cylinder in the small-size improvement process of the pump body structure is effectively solved.

On conventional double-cylinder rotor compressor pump body structure basis, this is disclosed through optimizing compressor pump body exhaust circulation passageway, effectively slows down the great air current pulsation and the aerodynamic noise that exhaust flow path arouses because of design space restriction and high frequency operation under the small-size high frequency double-cylinder compressor, greatly reduced compressor complete machine noise, improves compressor user listening experience. The specific implementation mode is as follows:

the noise experience feeling can still be ensured when the compressor is designed in a descending series mode when the compressor is operated at a higher frequency, the descending series mode means that the design space of an exhaust circulation channel (compared with the second exhaust circulation channel 111 disclosed by the invention) and the exhaust circulation area are further limited, the compressor operates at a high frequency, particularly under a heavy working condition, the gas flowing speed is high, the pneumatic noise is more serious, the overall noise of the compressor is greatly increased, and the compressor becomes one of the difficult problems which need to be solved urgently in the research and development process of the existing small high-frequency compressor product.

The problem that the pneumatic noise is large because of the small-size high frequency compressor exhaust circulation passageway design limitation arouses is focused on in this disclosure, and the innovation optimizes exhaust circulation passageway, effectively improves the air current pulsation of exhaust circulation passageway and the especially pneumatic noise that produces under the high frequency operation of double-cylinder compressor pump body, reaches small-size high frequency compressor low noise design purpose.

As shown in fig. 1-1d, the structure of the compressor pump body assembly, the exhaust gas flow path and the compressor pump body assembly according to the preferred embodiment of the present invention are respectively shown.

The innovative pump body assembly structure consists of a crankshaft 1, an upper flange assembly (comprising a first flange 2 (upper flange), an exhaust valve plate and a valve plate limiting baffle), a first silencer 3 (namely an upper silencer), a first roller 4 (namely an upper roller), a first cylinder 5 (upper cylinder), a first partition plate 61, a second partition plate 62, a second cylinder 7 (lower cylinder), a second roller 8 (lower roller), a lower flange assembly (comprising a second flange 9 (lower flange), an exhaust valve plate and a valve plate limiting baffle), a second silencer 10 (lower silencer) and a sliding sheet. Wherein, the first muffler 3 cooperates with upper flange to form the first silencing cavity 31, the second muffler 10 cooperates with lower flange to form the second silencing cavity 101, the first partition 61, the partition 6 that the second partition 62 assembles and forms has the third silencing cavity (namely middle cavity 100). The pump body assembly is provided with one or more exhaust circulation channels which axially penetrate through pump body parts such as upper and lower flanges, upper and lower cylinders, a partition plate assembly and the like, the third silencing cavity is arranged along the exhaust circulation channel, is communicated with the exhaust circulation channel and divides the exhaust circulation channel into a second exhaust circulation channel 111 and a first exhaust circulation channel 112 in two sections, the first silencing cavity 31 is communicated with an outlet of the first exhaust circulation channel 112, and the second silencing cavity 101 is communicated with an inlet of the second exhaust circulation channel 111.

The exhaust gas of the upper cylinder enters the first silencing cavity 31 from the first flange 2, and the exhaust gas of the lower cylinder passes through the second silencing cavity 101, then flows through the second exhaust passage 111, the middle cavity 100 and the first exhaust passage 112 in sequence to reach the first silencing cavity 31 to be merged with the upper exhaust gas, and then is exhausted outside the pump body from the exhaust port of the upper silencer (the gas flow path is shown by an arrow in fig. 1). Therefore, lower exhaust gas is silenced again by the middle cavity 100 in the process of passing through the exhaust circulation channel with smaller cross-sectional area, the larger airflow pulsation and pneumatic noise caused by the design space limitation and high-frequency operation of the exhaust circulation channel row are effectively reduced, the overall noise of the compressor is greatly reduced, and the auditory experience of a compressor user is improved.

1-1d, in some embodiments, the partition 6 includes a first partition 61 and a second partition 62, the first partition 61 is formed with a first cavity 200 inside, the second partition 62 is formed with a second cavity 300 inside, one axial side of the first partition 61 is connected to the first cylinder 5, one axial side of the second partition 62 is connected to the second cylinder 7, and the other axial side of the first partition 61 is connected to the other axial side of the second partition 62, such that the first cavity 200 is opposite to the second cavity 300 and is connected to form the intermediate cavity 100. This is the preferred structure form of the main embodiment of this disclosure, namely, through the concatenation of two baffles, can make the first cavity on the first baffle splice with the second cavity on the second baffle and form the middle chamber structure that is located in the middle, and the flow area of this embodiment is expanded and is reduced the change most obviously, and its noise elimination effect to the air current is also the best.

Referring to fig. 1-1d, there are shown a sectional view of the separator assembly of the present invention, three-dimensional line drawings of the first separator and the second separator, and schematic sectional structural diagrams thereof. The middle cavity 100 of the pump body assembly is an annular sealing cavity and is arranged on a partition plate assembly formed by matching a first partition plate 61 and a second partition plate 62, the first partition plate 61 is provided with a first opening end surface 612 and a first non-opening end surface 613, the second partition plate 62 is provided with a second opening end surface 622 and a second non-opening end surface 623, and the annular sinking cavity structure is characterized in that the first non-opening end surface 613 of the first partition plate 61 is matched with the lower end surface of a first cylinder 5, the second non-opening end surface 623 of the second partition plate is matched with the upper end surface of a second cylinder 7 to respectively seal the inner cavities of the upper cylinder and the lower cylinder, and the first opening end surface 612 of the first partition plate 61 is in contact fit with the second opening end surface 622 of the second partition plate 62 to form an annular sealed third silencing cavity (namely, the middle cavity 100). The bottom (non-open end face side) of the caisson structure of the first partition plate 61 and the second partition plate 62 is provided with one or more flow holes corresponding to the exhaust gas flow passages. The flow hole formed in the bottom of the first partition board 61 is the first flow outlet 611 of the middle chamber 100 and is communicated with the inlet of the corresponding first exhaust flow channel 112, and the flow hole formed in the bottom of the second partition board 62 is the first flow inlet 621 of the middle chamber 100 and is communicated with the outlet of the corresponding second exhaust flow channel 111. Preferably, the flow holes in the first partition plate and the second partition plate are tapered hole structures with cross-sectional flow areas gradually increasing toward the cavity direction, so that airflow pulsation at the inlet and outlet positions of the third silencing cavity can be effectively reduced, and aerodynamic noise is further reduced by optimization (a flow area gradual change structure is realized, and large airflow pulsation and flow loss caused by sudden change of the flow areas can be reduced).

In some embodiments, the first partition 61 is further provided with a first flow-through outlet 611, and one end of the first flow-through outlet 611 is communicated with the first cavity 200, and the other end is communicated with the first exhaust flow-through channel 112; the cross-sectional area of the first circulation outlet 611 is gradually reduced or constant from the junction with the first cavity 200 to the junction with the first exhaust circulation passage 112;

the second partition plate 62 is further provided with a first flow inlet 621, one end of the first flow inlet 621 is communicated with the second cavity 300, and the other end is communicated with the second exhaust circulation channel 111; the cross-sectional area of the first circulation outlet 611 is gradually reduced or constant from the junction with the second cavity 300 to the junction with the second exhaust circulation passage 111.

The gas in the middle cavity can be led out through the first circulation outlet arranged on the first partition plate, the gas can be led into the middle cavity through the first circulation inlet arranged on the second partition plate, and a transition section can be formed, so that the flow area formed between the middle cavity and the first exhaust circulation channel or the second exhaust circulation channel is not changed too much to cause airflow fluctuation, and the attenuation effect on airflow noise is improved; as shown in fig. 1a, the first flow inlet and the first flow outlet are tapered holes, so that the transition is smoother, as shown in fig. 5-5b, the first flow inlet and the first flow outlet are straight holes.

The middle cavity 100 (third silencing cavity) is an annular sealing cavity and is arranged on the partition plate assembly, the partition plate assembly is composed of a first partition plate and a second partition plate, the first partition plate and the second partition plate are of annular sinking cavity structures with opening end faces and non-opening end faces, the non-opening end faces of the first partition plate and the second partition plate are respectively matched with the lower end face of the upper cylinder and the upper end face of the lower cylinder, the inner cavities of the upper cylinder and the lower cylinder are sealed, and the opening ends of the first partition plate and the second partition plate are relatively matched to form the annular sealing third silencing cavity.

In some embodiments, the first cavity 200 is an annular counterbore and the second cavity 300 is an annular counterbore; and/or the first circulation inlet 621 has a trapezoidal or rectangular longitudinal cross-sectional shape, and the first circulation outlet 611 has a trapezoidal or rectangular longitudinal cross-sectional shape. This is the preferred form of construction of the main embodiment and the alternative embodiment of the present disclosure.

In some embodiments, if the inner diameter of the middle cavity is D1 and the inner diameter of the corresponding first cylinder or the second cylinder matched with the opening end face is D, the parameters D1 and D should satisfy: d1 > D. The effective sealing effect between the inner ring of the partition plate and the cylinder can be effectively guaranteed through the size. Preferably, the parameters D1 and D should satisfy: d1 > D + 5.

Alternative embodiments one to three, as shown in fig. 2 to 4a, in some embodiments, the partition plate 6 comprises a third partition plate 63, a third cavity 400 is formed inside the third partition plate 63, one axial side of the third partition plate 63 is connected with the first cylinder 5, the other axial side is connected with the second cylinder 7, and the third cavity 400 forms the intermediate chamber 100. This is the preferred form of construction for the alternative embodiment of the present disclosure, i.e., only 1 partition, i.e., the third partition, has only 1 cavity, i.e., the third cavity, within it, through which 1 cavity also the intermediate cavity structure for the expanding muffling can be formed.

2-2a, in some embodiments, a second flow outlet 631 is further disposed on the third partition 63, and one end of the second flow outlet 631 communicates with the third cavity 400 and the other end communicates with the first exhaust flow channel 112; the cross-sectional area of the second circulation outlet 631 is gradually reduced or constant from the junction with the third cavity 400 to the junction with the first exhaust circulation passage 112. This is the preferred form of construction of the first alternative embodiment of the present disclosure, i.e., the third partition plate has only the second flow-through outlet at the upper end, and the lower end of the third cavity is in direct communication with the second exhaust gas flow-through passage of the second cylinder.

In an alternative embodiment, as shown in fig. 3-3a, a second flow inlet 632 is further disposed on the third partition 63, and one end of the second flow inlet 632 is communicated with the third cavity 400, and the other end is communicated with the second exhaust gas flow channel 111; the cross-sectional area of the second flow-through inlet 632 decreases or does not change from the junction with the third cavity 400 to the junction with the second exhaust flow-through passage 111. This is the preferred form of construction of the second alternative embodiment of the present disclosure, i.e., the third partition has only the second flow opening at the lower end, and the upper end of the third cavity is in direct communication with the first exhaust gas flow passage of the first cylinder.

4-4a, in some embodiments, one end of the third cavity 400 is in communication with the first exhaust gas flow channel 112 and the other end is in communication with the second exhaust gas flow channel 111;

the structure further comprises at least two reinforcing ribs 64, wherein the at least two reinforcing ribs 64 are arranged in the third cavity 400 and are arranged at intervals along the circumferential direction of the third partition plate 63, and the third cavity 400 is divided into a plurality of small cavities along the circumferential direction.

This is the preferred configuration of the third alternative embodiment of the present disclosure, i.e., there is no transitional flow channel at both the upper and lower ends of the third partition, thus requiring the connection of the inner ring with the outer ring by means of the reinforcing ribs.

In some embodiments, the thickness of the reinforcing rib along the axial direction is set to be H, the inner diameter of the third cavity is set to be D2, the axial height of the third partition 63 is set to be H, the inner diameter of the first cylinder or the second cylinder is set to be D, and the parameters H, D2 and D are satisfied: h is less than H, D2 is more than D. H is less than H, so that the situation that the reinforcing rib structure obstructs the third silencing cavity and an invalid cavity structure occurs can be avoided; d2 is larger than D, so that the sealing of the cylinder cavity can be ensured.

In some embodiments, the parameters H, D2, D are such that: h is more than 2 and less than H-5, and D2 is more than D + 5. H is more than 2 and less than H-5: the cavity is made as large as possible while the strength of the reinforcing rib is ensured; d2 > D + 5: and the sealing distance of the inner cavity of the cylinder is ensured.

The present disclosure also provides a compressor including the pump body structure of any one of the foregoing.

The invention provides an innovative double-cylinder compressor pump body structure, an expanding noise elimination structure is designed on a circulation channel from lower exhaust to upper exhaust, thereby effectively slowing down airflow pulsation of a lower exhaust flow path of a double-cylinder compressor, greatly reducing pneumatic noise of the whole compressor, improving hearing experience of a compressor user,

the novel pump body assembly structure is not limited to the double-cylinder rotor compressor, and is also suitable for the rolling rotor compressors with similar lower exhaust structures, such as three cylinders, multiple cylinders and the like.

The present disclosure also provides an air conditioner including the compressor of any one of the preceding claims.

The utility model discloses focus to the big problem of pneumatic noise that the aforesaid arouses because of small-size high frequency compressor exhaust circulation passageway design limitation, provide a compressor with double-cylinder pump body subassembly structure, through optimizing exhaust passage, the expanding amortization runner of innovative design on exhaust circulation passageway effectively improves the air current pulsation of double-cylinder compressor pump body exhaust circulation passageway, the pneumatic noise of exhaust when greatly reduced compressor high frequency operation to a great extent improves compressor complete machine pneumatic noise.

The above description is only exemplary of the present disclosure and should not be taken as limiting the disclosure, as any modification, equivalent replacement, or improvement made within the spirit and principle of the present disclosure should be included in the scope of the present disclosure. The foregoing is only a preferred embodiment of the present disclosure, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present disclosure, and these modifications and variations should also be regarded as the protection scope of the present disclosure.