CN219366325U - Pump body assembly for compressor and compressor - Google Patents

Abstract

The application relates to the technical field of refrigeration equipment and discloses a pump body assembly for a compressor, which comprises a crankshaft, a cylinder, an upper flange, a lower flange and a silencing piece. The cylinder is provided with an airflow channel. The upper flange is sleeved on the crankshaft and connected with the upper end face of the cylinder, the upper flange is provided with a valve seat sinking groove, and an exhaust hole communicated with the air flow channel is arranged in the valve seat sinking groove. The lower flange is sleeved on the crankshaft and is connected with the lower end face of the cylinder. The silencing piece is arranged on the upper flange and surrounds the upper flange to form a silencing cavity, and the silencing cavity is communicated with the exhaust hole. Wherein, the valve seat sinking groove outer end is provided with the exhaust water conservancy diversion portion. Through being provided with exhaust water conservancy diversion portion at the disk seat heavy groove outer end, form the amortization structure that has interior intubate form with the amortization chamber, can eliminate the noise of more frequencies that produce in the compressor, the amortization effect is better, and then reduces the whole noise of compressor. The application also discloses a compressor.

Description

Pump body assembly for compressor and compressor

Technical Field

The application relates to the technical field of refrigeration equipment, for example, to a pump body assembly for a compressor and the compressor.

Background

In the refrigeration equipment system, a compressor is used to suck low-pressure refrigerant gas returned from an evaporator, compress the refrigerant gas to form high-temperature and high-pressure refrigerant gas, and discharge the refrigerant gas. The compressor consists of a pump body, a motor, a shell and a liquid separator component, wherein the process of compressing refrigerant gas from low pressure to high pressure is carried out in the pump body of the compressor, and the pump body mainly consists of a cylinder, a sliding vane, a crankshaft, rollers, an upper flange and a lower flange. For pump body components of a single exhaust structure, an exhaust port is generally formed in an upper flange. For the pump body component with the double exhaust structure, exhaust ports are formed in the upper flange and the lower flange. When the refrigerant gas is compressed to a certain pressure, the refrigerant gas is discharged from the exhaust port provided on the flange, and a large noise called air flow noise is generated when the refrigerant gas is discharged. In order to eliminate or reduce the air flow noise, in the related art, a muffler is added to the upper flange for the pump body of the single exhaust structure. For the pump body with the double exhaust structure, a silencer is added to both the upper flange and the lower flange. Among them, the muffler mounted on the upper flange is called an upper muffler, and the muffler mounted on the lower flange is called a lower muffler. The silencer is an expansion silencer, and mainly achieves the silencing effect through reflection effect generated by abrupt change of the inner section of a pipeline.

In the process of implementing the embodiments of the present disclosure, it is found that at least the following problems exist in the related art:

in the related art, the silencer is added on the flange to eliminate the air flow noise, and the expansion type resistant silencer can only eliminate the air flow noise with partial frequency, or has more air flow noise with other frequencies, so that the silencing effect is poor.

It should be noted that the information disclosed in the foregoing background section is only for enhancing understanding of the background of the present application and thus may include information that does not form the prior art that is already known to those of ordinary skill in the art.

Disclosure of Invention

The following presents a simplified summary in order to provide a basic understanding of some aspects of the disclosed embodiments. This summary is not an extensive overview, and is intended to neither identify key/critical elements nor delineate the scope of such embodiments, but is intended as a prelude to the more detailed description that follows.

The embodiment of the disclosure provides a pump body subassembly and compressor for compressor, through being provided with exhaust water conservancy diversion portion at the disk seat heavy groove outer end, the pump body subassembly that makes for the compressor has the effect of eliminating the noise better, and then reduces the whole noise of compressor, promotes user's use and experiences. The expansion type resistance silencer can only eliminate partial frequency airflow noise, and has the problems of more other frequency airflow noise and poor silencing effect.

In some embodiments, a pump body assembly for a compressor includes a crankshaft, a cylinder, an upper flange, a lower flange, and a muffler. The cylinder is provided with an airflow channel. The upper flange is sleeved on the crankshaft and connected with the upper end face of the cylinder, the upper flange is provided with a valve seat sinking groove, and an exhaust hole communicated with the air flow channel is arranged in the valve seat sinking groove. The lower flange is sleeved on the crankshaft and is connected with the lower end face of the cylinder. The silencing piece is arranged on the upper flange and surrounds the upper flange to form a silencing cavity, and the silencing cavity is communicated with the exhaust hole. Wherein, the valve seat sinking groove outer end is provided with the exhaust water conservancy diversion portion.

Optionally, the exhaust guiding part comprises a guiding cavity, and the depth of the guiding cavity is h1. The depth of the silencing cavity is H1, wherein H1/H1 is more than 0 and less than or equal to 3/4.

Optionally, the flow guiding cavity comprises a flow guiding wall, and at least part of the flow guiding wall forms a preset included angle with the vertical direction.

Optionally, the angle of the preset included angle is equal to 0 °. Or the angle of the preset included angle is larger than 0 degrees and smaller than or equal to 75 degrees, so that the flow guiding cavity is in a flaring shape from the upper flange to the silencing piece.

Optionally, the thickness of the guide wall is 0.5-2.0mm.

Alternatively, the thickness of the guide wall is 1.0-1.5mm.

Optionally, the valve seat sink includes a sink sidewall extending outwardly to form the exhaust guide.

Optionally, the pump body assembly further comprises a valve plate. The valve block is installed in the disk seat heavy groove, and the valve block is used for closing or opening the exhaust hole.

Optionally, a mounting hole is arranged in the valve seat sink adjacent to the exhaust hole, and the mounting hole is used for mounting the valve plate.

In some embodiments, the compressor includes a pump body assembly as described above for the compressor.

The pump body assembly for the compressor and the compressor provided by the embodiment of the disclosure can realize the following technical effects:

the pump body assembly for the compressor provided by the embodiment of the disclosure comprises a crankshaft, a cylinder, an upper flange, a lower flange and a silencing piece. Wherein, the upper flange is provided with a valve seat sinking groove, and an exhaust hole is arranged in the valve seat sinking groove. The cylinder is provided with an air flow channel which is communicated with an exhaust hole arranged in the valve seat sinking groove to form an exhaust channel of the pump body assembly, and the exhaust channel can be used for circulation of air flow in the compressor. The upper flange is provided with a silencing piece, and a silencing cavity is formed by surrounding the upper flange, so that noise of partial frequency generated when gas in the compressor flows through the exhaust passage is eliminated. Further, through being provided with exhaust water conservancy diversion portion at the disk seat heavy groove outer end, form the amortization structure that has interior intubate form with the amortization chamber, can eliminate the noise of more frequencies that produces when the gas flow in the compressor passes through exhaust flow channel, the amortization effect is better, and then reduces the whole noise of compressor, promotes user's use and experiences.

The foregoing general description and the following description are exemplary and explanatory only and are not restrictive of the application.

Drawings

One or more embodiments are illustrated by way of example and not limitation in the figures of the accompanying drawings, in which like references indicate similar elements, and in which like reference numerals refer to similar elements, and in which:

FIG. 1 is a schematic view of a pump body assembly for a compressor having an exhaust baffle provided in accordance with an embodiment of the present disclosure;

FIG. 2 is an enlarged schematic view of a portion of the area A of FIG. 1;

fig. 3 is a graph of sound transmission loss of a sound damping structure of a pump body assembly for a compressor having an exhaust guide part according to an embodiment of the present disclosure, wherein the preset included angles are 15 °, 45 °, 75 °;

fig. 4 is a schematic structural view of another pump body assembly for a compressor according to an embodiment of the present disclosure, where the preset included angle is 0 °;

FIG. 5 is a partially enlarged schematic illustration of region B of FIG. 4;

FIG. 6 is a graph of sound transmission loss of a sound deadening structure having an exhaust guide portion for a pump body assembly of a compressor according to an embodiment of the present disclosure, where the angle of the preset included angle is 0 °, and the depth of the guide chamber is half of the depth of the sound deadening chamber;

FIG. 7 is a schematic view of the upper flange of a pump body assembly for a compressor provided in accordance with an embodiment of the present disclosure;

fig. 8 is a schematic cross-sectional structure of the upper flange shown in fig. 7.

Reference numerals:

10: a crankshaft;

20: a cylinder; 21: an air flow channel;

30: an upper flange;

31: a valve seat sink groove; 311: an exhaust hole; 312: a mounting hole; 313: a sinking groove side wall;

32: an exhaust guide part; 321: a deflector wall;

40: a lower flange;

50: a sound deadening member; 51: a sound deadening chamber;

alpha: an included angle is preset.

Detailed Description

So that the manner in which the features and techniques of the disclosed embodiments can be understood in more detail, a more particular description of the embodiments of the disclosure, briefly summarized below, may be had by reference to the appended drawings, which are not intended to be limiting of the embodiments of the disclosure. In the following description of the technology, for purposes of explanation, numerous details are set forth in order to provide a thorough understanding of the disclosed embodiments. However, one or more embodiments may still be practiced without these details. In other instances, well-known structures and devices may be shown simplified in order to simplify the drawing.

The terms first, second and the like in the description and in the claims of the embodiments of the disclosure and in the above-described figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate in order to describe embodiments of the present disclosure. Furthermore, the terms "comprise" and "have," as well as any variations thereof, are intended to cover a non-exclusive inclusion.

In the embodiments of the present disclosure, the terms "upper", "lower", "inner", "middle", "outer", "front", "rear", and the like indicate an azimuth or a positional relationship based on that shown in the drawings. These terms are used primarily to better describe embodiments of the present disclosure and embodiments thereof and are not intended to limit the indicated device, element, or component to a particular orientation or to be constructed and operated in a particular orientation. Also, some of the terms described above may be used to indicate other meanings in addition to orientation or positional relationships, for example, the term "upper" may also be used to indicate some sort of attachment or connection in some cases. The specific meaning of these terms in the embodiments of the present disclosure will be understood by those of ordinary skill in the art in view of the specific circumstances.

In addition, the terms "disposed," "connected," "secured" and "affixed" are to be construed broadly. For example, "connected" may be in a fixed connection, a removable connection, or a unitary construction; may be a mechanical connection, or an electrical connection; may be directly connected, or indirectly connected through intervening media, or may be in internal communication between two devices, elements, or components. The specific meaning of the above terms in the embodiments of the present disclosure may be understood by those of ordinary skill in the art according to specific circumstances.

The term "plurality" means two or more, unless otherwise indicated.

In the embodiment of the present disclosure, the character "/" indicates that the front and rear objects are an or relationship. For example, A/B represents: a or B.

The term "and/or" is an associative relationship that describes an object, meaning that there may be three relationships. For example, a and/or B, represent: a or B, or, A and B.

It should be noted that, without conflict, the embodiments of the present disclosure and features of the embodiments may be combined with each other.

In the refrigeration equipment system, a compressor is used to suck low-pressure refrigerant gas returned from an evaporator, compress the refrigerant gas to form high-temperature and high-pressure refrigerant gas, and discharge the refrigerant gas. The compressor consists of a pump body, a motor, a shell and a liquid separator component, wherein the process of compressing refrigerant gas from low pressure to high pressure is carried out in the pump body of the compressor, and the pump body mainly consists of a cylinder, a sliding vane, a crankshaft, rollers, an upper flange and a lower flange. For pump body components of a single exhaust structure, an exhaust port is generally formed in an upper flange. For the pump body component with the double exhaust structure, exhaust ports are formed in the upper flange and the lower flange. When the refrigerant gas is compressed to a certain pressure, the refrigerant gas is discharged from the exhaust port provided on the flange, and a large noise called air flow noise is generated when the refrigerant gas is discharged.

In order to eliminate or reduce the air flow noise, in the related art, a muffler is added to the upper flange for the pump body of the single exhaust structure. For the pump body with the double exhaust structure, a silencer is added to both the upper flange and the lower flange. Among them, the muffler mounted on the upper flange is called an upper muffler, and the muffler mounted on the lower flange is called a lower muffler. The silencer is an expansion silencer, and mainly achieves the silencing effect through reflection effect generated by abrupt change of the inner section of a pipeline. The expansion type resistance silencer can only eliminate partial frequency airflow noise or more other frequency airflow noise by adding the silencer on the flange, and has poor silencing effect.

According to the pump body assembly for the compressor and the compressor, the exhaust guide part 32 is arranged at the outer end of the valve seat sinking groove 31, so that the pump body assembly for the compressor has the effect of better eliminating noise, the overall noise of the compressor is reduced, and the use experience of a user is improved. The expansion type resistance silencer can only eliminate partial frequency airflow noise, and has the problems of more other frequency airflow noise and poor silencing effect.

As shown in connection with fig. 1-8, a pump body assembly for a compressor provided in an embodiment of the present disclosure includes a crankshaft 10, a cylinder 20, an upper flange 30, a lower flange 40, and a muffler 50. A cylinder 20 is provided to the crankshaft 10, and the cylinder 20 is provided with an airflow passage 21. The upper flange 30 is sleeved on the crankshaft 10 and is connected with the upper end face of the cylinder 20, the upper flange 30 is provided with a valve seat sinking groove 31, and an exhaust hole 311 communicated with the air flow channel 21 is arranged in the valve seat sinking groove 31. The lower flange 40 is sleeved on the crankshaft 10 and connected with the lower end surface of the cylinder 20. The muffler 50 is disposed on the upper flange 30, and surrounds the upper flange 30 to form a muffler cavity 51, and the muffler cavity 51 is communicated with the exhaust hole 311. Wherein, the outer end of the valve seat sinking groove 31 is provided with an exhaust diversion part 32.

For better understanding, the bottom of the valve seat sink 31 is taken as the inner end of the valve seat sink 31, and the upper end of the sink sidewall 313 of the valve seat sink 31 is contacted with the outer end of the valve seat sink 31.

By adopting the pump body assembly for the compressor, which is provided by the embodiment of the disclosure, the air flow noise generated in the compressor with more frequencies can be eliminated, and the silencing effect is better. The pump body assembly for a compressor provided in the embodiment of the present disclosure includes a crankshaft 10, a cylinder 20, an upper flange 30, a lower flange 40, and a muffler 50. Wherein, the upper flange 30 is provided with a valve seat sinking groove 31, and an exhaust hole 311 is arranged in the valve seat sinking groove 31. The cylinder 20 is provided with an air flow passage 21 which is communicated with an exhaust hole 311 arranged in the valve seat sinking groove 31 to form an exhaust passage of the pump body assembly, and can be used for circulating air flow in the compressor. The upper flange 30 is provided with a muffler 50 and a muffler chamber 51 is formed around the upper flange 30 to eliminate noise of a partial frequency generated when gas in the compressor flows through the discharge passage. Further, through being provided with exhaust water conservancy diversion portion 32 at the disk seat heavy groove 31 outer end, form the amortization structure that has interior intubate form with amortization chamber 51, can eliminate the noise of more frequencies that produces when the gas flow in the compressor passes through exhaust flow channel 21, the amortization effect is better, and then reduces the whole noise of compressor, promotes user's use experience.

Specifically, as shown in conjunction with fig. 1 and 4, the exhaust gas guiding portion 32 and the sound deadening chamber 51 form a resistant sound deadening structure having an inner insertion pipe type. The direction of the arrow in the drawing is the direction of the air flow in the compressor, so that the air flow in the compressor flows from the air flow passage 21 of the cylinder 20 to the exhaust hole 311 of the upper flange 30, and then is discharged into the muffler chamber 51 through the exhaust guide 32, and finally is discharged from the air hole of the muffler 50. Since the exhaust guide part 32 and the silencing cavity 51 form a resistant silencing structure with an inner cannula form, more frequency airflow noise generated by the compressor can be eliminated, and the effect of eliminating the airflow noise generated by the compressor is better.

Optionally, the exhaust guide portion 32 includes a guide cavity having a depth h1. The depth of the silencing cavity 51 is H1, wherein H1/H1 is more than 0 and less than or equal to 3/4.

The depth of the flow guiding cavity is set to be H1, the depth of the silencing cavity 51 is set to be H1, and H1/H1 is more than 0 and less than or equal to 3/4. That is, the length of the flow guiding chamber cannot exceed the depth of the sound deadening chamber 51/4 at maximum. Therefore, on the basis of not affecting the self silencing effect of the silencing cavity 51, the exhaust guide part 32 and the silencing cavity 51 form a resistant silencing structure with an inner inserting pipe mode, and further the effect of eliminating airflow noise generated by the compressor is better.

Further, if the length of the flow guiding chamber exceeds the maximum 3/4 of the depth of the sound deadening chamber 5, the distance from the exhaust flow guiding portion 32 to the upper wall surface of the sound deadening member 50 is too short, which affects the elimination effect of the sound deadening member 50 itself on the noise generation of the air flow generated by the compressor.

Optionally, the guiding cavity includes a guiding wall 321, and the guiding wall 321 forms a preset included angle α with the vertical direction at least partially.

It is understood that the guide wall 321 may be at least partially located at a portion of the circumference of the exhaust hole 311. And because part of the guide wall 321 of the guide cavity is closer to the crankshaft, the part can be vertically upwards arranged. The angle of the guide wall 321 at least partially forms a preset included angle α with the vertical direction is not limited, and may be set according to the actual application requirement of the user.

Specifically, the guide wall 321 of the guide cavity is set to form a preset included angle α with the vertical direction, so that the exhaust guide can be set into different structural forms. Specifically, the valve seat recess 31 may be cylindrical or tapered, and the opening with the larger taper faces away from the bottom of the valve seat recess. Therefore, on the basis that the exhaust guide part 32 and the silencing cavity 51 form a resistance silencing structure with an inner inserting pipe form to enhance and eliminate the airflow noise effect generated by the compressor, the exhaust guide can be set into different structural forms, so that the compressor can meet different use scenes, and more choices are provided for users.

Optionally, the angle of the preset angle α is equal to 0 °. Or, the angle of the preset included angle alpha is larger than 0 degrees and smaller than or equal to 75 degrees, so that the flow guiding cavity is in a flaring shape from the upper flange 30 to the direction of the silencing piece 50.

By setting the angle of the preset included angle alpha between the guide wall 321 and the vertical direction to be more than or equal to 0 degrees and less than or equal to 75 degrees, the exhaust guide part 32 and the silencing cavity 51 can form a resistant silencing structure with an inner inserting tube form, and the silencing effect on airflow noise generated by the compressor is better.

Specifically, the angle of the preset included angle α between the guide wall 321 and the vertical direction may be 0 °, 15 °, 25 °, 35 °, 45 °, 55 °, 65 °, 75 °.

When the angle α between the guide wall 321 and the vertical direction is 0 °, the exhaust guide portion 32 has a cylindrical structure, as shown in fig. 4. The direction of the arrow in fig. 4 is the direction of the air flow in the compressor, so that the air flow in the compressor flows from the air flow passage 21 of the cylinder 20 to the exhaust hole 311 of the upper flange 30, and then is discharged into the sound deadening chamber 51 through the exhaust guide 32, and finally is discharged from the air hole of the muffler. When the depth of the guide chamber is 1/2 of the depth of the sound deadening chamber 51 as shown in fig. 5, the passing frequency of the odd multiple of 1/2 wavelength noise can be eliminated as shown in fig. 6. The portion shown by the broken line in fig. 6 is the frequency of the noise to be eliminated. When the depth of the guide chamber is 1/4 of the depth of the sound deadening chamber 51, the passing frequency of even multiple of 1/2 wavelength noise can be eliminated. The resistive sound deadening structure having the form of the cylindrical inner insertion pipe formed by the cylindrical exhaust guide 32 and the sound deadening chamber 51 thus eliminates more frequent air flow noise generated by the compressor, thereby enhancing the sound deadening effect on the air flow noise generated by the compressor.

When the angle α between the guide wall 321 and the vertical direction is greater than 0 ° and less than or equal to 75 °, the exhaust guide portion 32 has a conical structure, as shown in fig. 1, i.e. the guide cavity is flared from the upper flange toward the muffler. The direction of the arrow in fig. 1 is the direction of the air flow in the compressor, so that the air flow in the compressor flows from the air flow passage 21 of the cylinder 20 to the exhaust hole 311 of the upper flange 30, and then is discharged into the sound deadening chamber 51 through the exhaust guide 32, and finally is discharged from the air hole of the muffler. Since the flow passing section at the discharge port suddenly becomes larger or smaller, a vortex flow is caused to generate new noise, and the noise generated with an increase in the discharge amount and discharge speed of the compressor is also increased. The exhaust guide 32 of the inner insert pipe structure is provided to have an inner cone structure, which can reduce the generation of new noise and further improve the effect of noise elimination, thereby reducing the overall noise of the compressor.

Further, since the length of the flow guiding chamber is greater than 0 and less than or equal to the depth of the sound deadening chamber 513/4. When the length of the flow guiding chamber is selected to be close to or equal to the depth of the silencing chamber 513/4, the distance from the exhaust guiding portion 32 to the side wall surface of the silencing member 50 becomes closer as the angle of the preset angle α between the guiding wall 321 and the vertical direction increases. Therefore, when the angle between the guide wall 321 and the vertical direction is too large, the distance from the exhaust guide portion 32 to the side wall surface of the silencer 50 is too short, which affects the elimination effect of the silencer 50 on the noise generated by the compressor.

As shown in fig. 2 and 3, as the angle of the guide wall 321 with respect to the vertical direction is increased by a predetermined angle α, the noise transmission loss of high frequency increases, i.e., the high frequency noise generated by the compressor is better removed by the resistive sound deadening structure having the form of the tapered inner cannula formed by the tapered exhaust guide part 32 and the sound deadening chamber 51. The user can reasonably customize and set the angle of the preset included angle alpha between the guide wall 321 and the vertical direction according to the actual application requirement.

Alternatively, the thickness of the guide wall 321 is 0.5-2.0mm.

By setting the thickness of the guide wall 321 to 0.5-2.0mm, the strength of the exhaust guide portion 32 can be made to satisfy the exhaust demand in the compressor on the basis that the formation of the resistant sound deadening structure having the form of an inner pipe with the exhaust guide portion 32 and the sound deadening chamber 51 enhances the effect of eliminating noise generated by the compressor.

Specifically, the thickness of the guide wall 321 may be 0.5mm, 0.8mm, 1.0mm, 1.3mm, 1.5mm, 1.8mm, 2.0mm.

When the thickness of the guide wall 321 is set to be greater than 2.0mm, the distance from the exhaust guide portion 32 to the side wall surface of the silencing cavity 51 is relatively short, which may affect the effect of the silencing member 50 on eliminating noise generated by the compressor, and increasing the thickness of the guide wall 321 may increase the cost.

When the thickness of the guide wall 321 is set to be less than 0.5mm, high pressure airflow is generated in the compressor and flows through the exhaust guide portion 32, and the strength of the thinner guide wall 321 may not be enough to meet the exhaust requirement in the compressor, so that the exhaust guide portion 32 may be damaged, and the silencing effect of airflow noise generated in the compressor is further affected.

Alternatively, the thickness of the guide wall 321 is 1.0-1.5mm.

By setting the thickness of the guide wall 321 to 1.0-1.5mm, it is found from the results of experiments performed by the developer that the performance of the exhaust guide portion 32 can be optimized by selecting the thickness of the guide wall 321 within this range.

Specifically, the thickness of the guide wall 321 may be 1.0mm, 1.1mm, 1.2mm, 1.3mm, 1.4mm, 1.5mm.

In practical applications, the wall thickness of the silencer 50 is generally set to 1.0mm, and the strength of the silencer 50 can meet the silencing and exhausting requirements of the air flow in the compressor, so the thickness of the guide wall 321 of the exhaust guide portion 32 can be set to 1.2mm.

As shown in connection with fig. 7 and 8, the upper flange 30 is shown having a cylindrical exhaust baffle portion 32. It can be seen that the guide wall 321 of the exhaust guide 32 is further away from the wall surface of the silencer 50 in the drawing, and the thickness of the guide wall 321 is also set relatively thin on the basis of meeting the silencing and exhausting requirements of the air flow in the compressor.

Optionally, the valve seat sink 31 includes a sink sidewall 313, the sink sidewall 313 extending outwardly to form the exhaust guide 32.

The exhaust guide portion 32 is formed by extending the side wall 313 of the seat recess 31 outward, that is, the exhaust guide portion 32 and the side wall of the seat recess 31 are integrally formed, so that the exhaust guide portion 32 and the upper flange 30 are integrated. The exhaust guide portion 32 is used as a part of the upper flange 30, and is not required to be assembled and fixed by using a connecting piece, so that the integral structure of the upper flange 30 is more stable and is not easy to damage.

Further, in the production process of the upper flange 30, since the exhaust guide portion 32 is a part of the upper flange 30, it is not necessary to use an additional production mold to separately produce the exhaust guide portion 32, so that the production process is simpler and more cost is saved.

Optionally, the pump body assembly further comprises a valve plate. The valve plate is installed in the valve seat sink 31, and the valve plate is used for closing or opening the exhaust hole.

So arranged, the valve plate is mounted to the valve seat sink 31 for closing or opening the exhaust hole 311. Thus, when the refrigerant gas in the compressor is compressed to a certain pressure, the valve sheet opens the exhaust hole 311 of the upper flange 30 to discharge the gas. When the discharge of the refrigerant gas in the compressor is not required, the valve sheet is closed to the discharge hole 311.

Optionally, a mounting hole 312 is disposed in the valve seat sink 31 adjacent to the exhaust hole 311, and the mounting hole 312 is used for mounting the valve plate.

Mounting holes 312 are formed in the valve seat sink 31 adjacent to the exhaust holes 311 for mounting the valve plate, so that the valve plate and the valve seat sink 31 can be more stably fixed. Further, the mounting holes 312 can provide accurate positioning for mounting the valve plate, so that the mounting process of the valve plate is more convenient, and the working time of the installer is saved.

Specifically, an exhaust guide portion 32 is provided at the outer end of the valve seat sink 31 in the present application. The pump body assembly is not only suitable for the pump body assembly with a single exhaust structure, but also suitable for the pump body assembly with a double exhaust structure. And is not limited to the upper flange 30, and both the upper flange 30 and the lower flange 40 may be applicable.

In some embodiments, the compressor includes a pump body assembly as described above for the compressor.

The above description and the drawings illustrate embodiments of the disclosure sufficiently to enable those skilled in the art to practice them. Other embodiments may include structural and other modifications. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the sequence of operations may vary. Portions and features of some embodiments may be included in, or substituted for, those of others. The embodiments of the present disclosure are not limited to the structures that have been described above and shown in the drawings, and various modifications and changes may be made without departing from the scope thereof. The scope of the present disclosure is limited only by the appended claims.

Claims (10)

1. A pump body assembly for a compressor, comprising:

a crankshaft;

the cylinder is arranged on the crankshaft and is provided with an airflow channel;

the upper flange is sleeved on the crankshaft and connected with the upper end face of the air cylinder, the upper flange is provided with a valve seat sinking groove, and an exhaust hole communicated with the air flow channel is arranged in the valve seat sinking groove;

the lower flange is sleeved on the crankshaft and connected with the lower end face of the cylinder; and, a step of, in the first embodiment,

the silencing piece is arranged on the upper flange and surrounds the upper flange to form a silencing cavity, the silencing cavity is communicated with the exhaust hole,

wherein, the valve seat sinks the groove outer end and is provided with exhaust water conservancy diversion portion.

2. The pump body assembly of claim 1, wherein,

the exhaust diversion part comprises a diversion cavity, and the depth of the diversion cavity is h1;

the depth of the silencing cavity is H1,

wherein H1/H1 is more than 0 and less than or equal to 3/4.

3. The pump body assembly of claim 2, wherein,

the flow guiding cavity comprises a flow guiding wall, and at least part of the flow guiding wall forms a preset included angle with the vertical direction.

4. The pump body assembly of claim 3, wherein,

the angle of the preset included angle is equal to 0 degree; or alternatively, the process may be performed,

the angle of the preset included angle is larger than 0 degree and smaller than or equal to 75 degrees, so that the flow guiding cavity is in a flaring shape from the upper flange to the silencing piece.

5. The pump body assembly of claim 3, wherein,

the thickness of the guide wall is 0.5-2.0mm.

6. The pump body assembly of claim 5, wherein the pump body assembly comprises,

the thickness of the guide wall is 1.0-1.5mm.

7. The pump body assembly of any one of claims 1 to 6, wherein,

the valve seat sinking groove comprises a sinking groove side wall, and the sinking groove side wall extends outwards to form an exhaust diversion part.

8. The pump body assembly of any one of claims 1 to 6, further comprising:

and the valve plate is arranged in the valve seat sink groove and is used for closing or opening the exhaust hole.

9. The pump body assembly of claim 8, wherein,

and a mounting hole is formed in the valve seat sink adjacent to the exhaust hole and is used for mounting the valve plate.

10. A compressor comprising a pump body assembly for a compressor according to any one of claims 1 to 9.