CN111287968A - Compressor and refrigeration equipment - Google Patents

Compressor and refrigeration equipment Download PDF

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Publication number
CN111287968A
CN111287968A CN201811504407.2A CN201811504407A CN111287968A CN 111287968 A CN111287968 A CN 111287968A CN 201811504407 A CN201811504407 A CN 201811504407A CN 111287968 A CN111287968 A CN 111287968A
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CN
China
Prior art keywords
air
valve assembly
valve plate
air valve
assembly groove
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Granted
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CN201811504407.2A
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Chinese (zh)
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CN111287968B (en
Inventor
曹培森
吴延平
曹小军
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Guangdong Meizhi Precision Manufacturing Co Ltd
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Guangdong Meizhi Precision Manufacturing Co Ltd
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Priority to CN201811504407.2A priority Critical patent/CN111287968B/en
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Publication of CN111287968B publication Critical patent/CN111287968B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3566—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along more than line or surface
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

The invention provides a compressor and refrigeration equipment, wherein an air valve assembly is arranged in an air valve assembly groove of an air cylinder, the air valve assembly, a sliding sheet and the sliding sheet groove define a second working cavity, the air valve assembly comprises a valve plate, and the valve plate is provided with a second air suction port and a second air exhaust port which are communicated with the second working cavity; wherein, the height of the cylinder is HA1, the height of the valve plate is HB1, and the value is more than 0 (HA1-HB1) and less than or equal to 45 μm. According to the compressor provided by the invention, if the valve plate is higher than the cylinder, the matching clearance between the upper bearing and the lower bearing of the compressor and the cylinder cannot be ensured, so that the risk of leakage is caused, and the sealing property of the second working cavity is influenced; if the height of the valve plate is lower than that of the cylinder but the height difference between the valve plate and the cylinder is too large, the second working chamber is communicated with high-back-pressure gas in the shell of the compressor, so that the performance is low, and the performance of the compressor, particularly the heating capacity at low temperature, is influenced.

Description

Compressor and refrigeration equipment
Technical Field
The invention relates to the technical field of compressors, in particular to a compressor and refrigeration equipment comprising the same.
Background
A sliding vane tail compression structure appears in the existing industry, can be used as a second compression cavity, and has the technical characteristics of high energy efficiency, low cost and the like. However, the tail compression structure as an independent compression chamber needs to have strict technical requirements such as size relation and the like. The unreasonable size relationship easily brings the problems of low energy efficiency, high noise, poor reliability, high cost and the like.
Disclosure of Invention
The present invention is directed to solving at least one of the problems of the prior art.
To this end, an aspect of the present invention is directed to a compressor.
Another aspect of the present invention is directed to a refrigerating apparatus including the above compressor.
To achieve the above object, an aspect of the present invention provides a compressor, including: a cylinder having a first working chamber, a slide groove, and a valve assembly groove, the first working chamber having a first intake port and a first exhaust port; the piston is eccentrically and rotatably arranged in the first working cavity; the sliding sheet can be arranged in the sliding sheet groove in a reciprocating motion mode, and the front end of the sliding sheet is abutted against the piston; the air valve assembly is arranged in the air valve assembly groove, a second working cavity is defined by the air valve assembly, the sliding sheet and the sliding sheet groove, the air valve assembly comprises a valve plate, and the valve plate is provided with a second air suction port and a second air exhaust port which are communicated with the second working cavity; wherein the height of the cylinder is HA1, the height of the valve plate is HB1, and the value is more than 0 (HA1-HB1) and less than or equal to 45 mu m.
According to the compressor provided by the technical scheme, the piston can be arranged in the compression cavity in a rolling manner, the working medium is sucked from the first air suction port, the piston rolls along the inner wall of the air cylinder cavity to compress the working medium, and the compressed working medium is discharged from the first air discharge port.
In the second working chamber, the sliding sheet reciprocates relative to the sliding sheet groove under the drive of the piston, the second working chamber can perform periodic cycle work such as air suction, compression, exhaust and the like through the movement of the sliding sheet, specifically, a working medium is sucked from the second air suction port and compressed in the second working chamber, and is discharged from the second air outlet after the pressure reaches the exhaust pressure.
0 < (HA1-HB1) is less than or equal to 45 mu m, and if the valve plate is higher than the cylinder, the fit clearance between the upper bearing and the lower bearing of the compressor and the cylinder cannot be ensured, so that the risk of leakage is caused, and the sealing property of the second working chamber is influenced; if the height of the valve plate is lower than that of the cylinder but the height difference between the valve plate and the cylinder is too large, the second working chamber is communicated with high-back-pressure gas in the shell of the compressor, so that the performance is low, and the performance of the compressor, particularly the heating capacity at low temperature, is influenced.
In addition, the compressor provided by the technical scheme of the invention also has the following additional technical characteristics:
in the above technical solution, preferably, the air valve assembly further includes an air suction valve sheet disposed on the valve plate, the air suction valve sheet is used for opening and closing the second air suction port, and the height of the air suction valve sheet is HC1, and 0 < (HA1-HC1) > is less than or equal to 4 mm.
If the air suction valve plate is higher than the air cylinder, the matching clearance between an upper bearing and a lower bearing of the compressor and the air cylinder cannot be guaranteed, the risk of leakage is caused, and the sealing performance of the second working cavity is influenced, wherein the upper bearing and the lower bearing are respectively arranged above and below the air cylinder, and the upper bearing, the lower bearing, the sliding sheet groove, the air suction valve plate and the valve plate jointly define the second working cavity; if the height of the air suction valve plate is lower than that of the cylinder but the height difference between the air suction valve plate and the cylinder is too large, the second working cavity is communicated with high-backpressure air in the shell of the compressor, so that the performance is low, and the performance of the compressor, particularly the heating capacity at low temperature, is influenced.
In the technical scheme, preferably 0 < (HA1-HC1) ≦ 45 μm.
In the above technical solution, preferably, the tail end of the air valve assembly groove is of a non-open structure, and the thickness of the tail end of the air valve assembly groove is SA2, so SA2 is greater than or equal to 1.5 mm; and/or the tail end of the air valve assembly groove is of a non-open structure, the thickness of the valve plate is SB1, the thickness of the air valve assembly groove is SA1, and SA1 is greater than SB1 and is larger than or equal to 3 mm.
The position far away from the center of the cylinder is a tail end, the tail end of the air valve assembly groove is in a non-open structure, namely SA2 is not equal to 0, in other words, the air valve assembly groove is in a closed structure. The thickness of the tail end of the air valve assembly groove is ensured to be enough by more than or equal to 1.5mm of SA2, so that the strength of the tail end of the air valve assembly groove is ensured, and the deformation of the tail end of the air valve assembly groove due to too low strength is avoided.
On the valve plate of sealed tube and expansion pipe interference fit, SA1 > SB1 is more than or equal to 3mm, and valve plate and sealed tube and expansion pipe need satisfy certain cooperation distance in order to guarantee sealed length, if cooperation length is less than 3mm, then the phenomenon such as performance hypo, second working chamber breathing pipe overheat are caused to high-pressure gas link up with second working chamber breathing pipe in the casing. The compressor comprises a shell and a compression mechanism positioned in the shell, wherein the compression mechanism comprises a cylinder, a piston, an eccentric crankshaft, a sliding sheet and an air valve assembly.
In the above technical scheme, preferably, the tail end of the air valve assembly groove is of a non-open structure, the thickness of the air valve assembly groove is SA1, the thickness of the valve plate is SB1, the air valve assembly further comprises an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, the thickness of the air suction valve plate is SC1, and then SA1- (SB1+ SC1) is not more than 0.05mm and not more than 5 mm.
SA1- (SB1+ SC1) ≥ 0.05mm to guarantee the installation clearance of valve plate and air valve assembly groove, SA1- (SB1+ SC1) ≤ 5mm, avoid the too big installation clearance of valve plate and air valve assembly groove, have great influence to the noise that air current brought in air valve assembly groove department.
In the above technical solution, preferably, the tail end of the air valve assembly groove is of a non-open structure, the length of the air valve assembly groove is LA1, and the length of the valve plate is LB1, so that LB1 is not more than (LA1-0.05mm), which facilitates the installation of the valve plate in the air valve assembly groove.
In the above technical scheme, preferably, the tail end of the air valve assembly groove is of a non-open structure, the length of the valve plate is LB1, the air valve assembly further includes an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, the width of the air suction valve plate is LC1, and LC1 is not more than LB1, so that the air suction valve plate can conveniently control the opening and closing of the second air suction port.
In the above technical solution, preferably, the valve assembly groove is of an open structure, that is, one end of the valve assembly groove is open, for example, the valve assembly groove is open toward the tail end of the valve assembly (at this time, SA2 ═ 0), or the valve assembly groove is open toward a side of the valve assembly facing away from the first air intake, or the valve assembly groove is open toward a side of the valve assembly facing toward the first air intake.
In the above technical solution, preferably, one side of the air valve assembly groove facing the air valve assembly is an open structure; and/or one side of the air valve assembly groove, which faces the air valve assembly and is back to the first air suction port, is of an open structure.
In the above technical solution, preferably, when one side of the air valve assembly groove facing the air valve assembly is of an open structure, the air valve assembly groove facing the tail end of the air valve assembly is processed in a grinding manner to improve the processing accuracy; and/or when one side of the air valve assembly groove, which faces the air valve assembly and is back to the first air suction port, is of an open structure, the surface of the air valve assembly groove, which faces the side of the air valve assembly, which is back to the first air suction port, is processed in a grinding mode, so that the processing precision is improved.
In the above technical solution, preferably, the thickness of the air valve assembly groove is SA1, the thickness of the valve plate is SB1, then SA1 > SB1 is greater than or equal to 3mm, SA1 refers to a connection line from an end surface of the air valve assembly groove matched with the air valve assembly (an end surface of the air valve assembly groove close to the sliding vane) as a starting point, a direction perpendicular to the end surface of the air valve assembly groove matched with the air valve assembly groove and the air valve assembly is P, and the connection line passes through the end surface of the valve plate departing from the first air suction port to the inner diameter of the main casing of the compressor. Preferably, the valve plate is rectangle, including the first limit that connects gradually, the second limit, third limit and fourth edge, first limit and third limit extend along the length direction of valve plate, second limit and fourth edge extend along the width direction of valve plate, first limit is close to the gleitbretter setting, the second limit sets up to first air intake dorsad, use the crossing point M of the extension line on second limit and the terminal surface towards first limit on the pneumatic valve assembly as the starting point, the second limit extends, and extend to main casing internal diameter Q point along the direction on second limit, SA1 is MQ, wherein the cylinder is located the main casing of compressor.
SA1 > SB1 ≧ 3mm because: the valve plate, the sealing pipe and the expansion pipe need to meet a certain matching distance to guarantee the sealing length, and if the matching length is less than 3mm, high-pressure gas in the shell is communicated with the second working cavity air suction pipe to cause the phenomena of low performance, overheating of the second working cavity air suction pipe and the like.
In the above technical scheme, preferably, the air valve assembly further includes an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, the thickness of the air suction valve plate is SC1, and SA1- (SB1+ SC1) is not less than 0.05mm because it is required to ensure that a gap of at least 0.05mm is ensured between the pump body and the inner diameter of the housing after assembly, thereby avoiding interference between the pump body and the housing.
In the above technical solution, preferably, a side of the air valve assembly groove facing the air valve assembly is an open structure, a side of the air valve assembly groove facing the air valve assembly and away from the first air intake port is an open structure, a length of the air valve assembly groove is LA1, and a length of the valve plate is LB1, where LA1 is greater than or equal to 0.5LB1 and less than or equal to 2LB 1. LA1 is the length of the end of the valve assembly groove that mates with the valve assembly.
In the above technical solution, preferably, one side of the air valve assembly groove facing the air valve assembly is an open structure, the length of the air valve assembly groove is LA1, the length of the valve plate is LB1, and LB1 is not more than (LA1-0.05 mm).
When one side of the air valve component groove facing the air valve component is of an open structure and one side of the air valve component groove facing the air valve component and back to the first air suction port is of a non-open structure, LB1 is less than or equal to (LA1-0.05mm), and the valve plate is convenient to mount in the air valve component groove.
In the above technical solution, preferably, one side of the air valve assembly groove facing the air valve assembly is in an open structure, the air valve assembly further includes an air suction valve plate disposed on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, and if the width of the air suction valve plate is LC1, LC1 is not less than LB 1.
When one side of the air valve assembly groove facing the air valve assembly is of an open structure, and one side of the air valve assembly groove facing the air valve assembly and back to the first air suction port is of a non-open structure, the LB1 with the liquid level ratio of LC1 being equal to or less than that of the LB1 facilitates the control of the air suction valve plate on the opening and closing of the second air suction port.
In the above technical solution, preferably, the minimum distance from the valve assembly groove to the first air intake port is LA3, and LA3 is greater than or equal to 0.5 mm.
An aspect of a second aspect of the present invention provides a refrigeration apparatus comprising a compressor as described in any one of the aspects of the first aspect.
The refrigeration equipment provided by the technical scheme of the second aspect of the present invention includes the compressor described in any one of the technical schemes of the first aspect, so that all the beneficial effects of the compressor described in any one of the technical schemes are achieved, and details are not repeated herein.
In the description of the present invention, it should be noted that the "refrigeration equipment" mentioned in the present invention may include any device capable of refrigerating to which the technical solution of the present invention can be applied, including, but not limited to, a refrigerator, an air conditioner or a central air conditioner.
Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
fig. 1 is a schematic structural view of a compressor according to a first embodiment of the present invention;
FIG. 2 is a schematic sectional view taken along line A-A in FIG. 1;
fig. 3 is a schematic structural view of a compressor according to a first embodiment of the present invention;
FIG. 4 is a schematic structural diagram of a cylinder according to a first embodiment of the present invention;
FIG. 5 is a schematic structural diagram of a cylinder according to a first embodiment of the present invention;
fig. 6 is a schematic structural view of a compressor according to a second embodiment of the present invention;
FIG. 7 is a schematic cross-sectional view taken along line C-C of FIG. 6;
fig. 8 is a schematic structural view of a compressor according to a second embodiment of the present invention;
fig. 9 is a schematic structural diagram of a compressor according to a third embodiment of the present invention.
Wherein, the correspondence between the reference numbers and the part names in fig. 1 to 9 is:
the air cylinder comprises a cylinder 1, a cylinder cavity 11, a first air suction port 12, a sliding sheet groove 14, a valve assembly groove 15, a first working cavity 16, an air suction cavity 17, an air exhaust cavity 18, a piston 2, a sliding sheet 3, a front end 31, a tail end 32, an air suction valve sheet 4, a valve plate 5, a first edge 51, a second edge 52, a lift limiter 6 and a second working cavity 7.
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced otherwise than as specifically described herein, and thus the scope of the present invention is not limited by the specific embodiments disclosed below.
A compressor and a refrigerating apparatus according to some embodiments of the present invention will be described below with reference to the accompanying drawings.
As shown in fig. 1, a compressor according to some embodiments of the present invention includes a cylinder 1, a piston 2, a vane 3, and a valve assembly. The cylinder 1 is provided with a first working chamber 16, a slide plate groove 14 and a valve assembly groove 15, wherein the first working chamber 16 is provided with a first air suction port 12 and a first air discharge port; the piston 2 is eccentrically and rotatably arranged in the first working chamber 16; the sliding vane 3 is reciprocally disposed in the sliding vane slot 14, the front end 31 of the sliding vane 3 is stopped against the piston 2, as shown in fig. 2, HD1 is the height of the sliding vane, as shown in fig. 5, the sliding vane slot width is K; the air valve assembly is arranged in the air valve assembly groove 15, the second working cavity 7 is limited by the air valve assembly, the sliding sheet 3 and the sliding sheet groove 14, the air valve assembly comprises a valve plate 5, and the valve plate 5 is provided with a second air suction port and a second air exhaust port which are communicated with the second working cavity 7.
The cylinder 1 is provided with a compression cavity, the piston 2 is rotatably arranged in the compression cavity, the front end 31 of the sliding sheet 3 is abutted against the piston 2, and the tail end 32 of the sliding sheet 3 is positioned in the sliding sheet groove 14. The piston 2, the sliding vane 3 and the cylinder cavity 11 define a first working cavity 16, the piston 2 and the sliding vane 3 divide the first working cavity 16 into a suction cavity 17 and an exhaust cavity 18, the suction cavity 17 is provided with a first suction port 12, and the exhaust cavity 18 is provided with a first exhaust port.
The valve plate 5 has the second suction port that can open and close and communicate with second working chamber 7 and has the second gas vent that communicates with second working chamber 7, the air valve assembly is still including setting up the suction valve block 4 that is used for the switching second suction port on valve plate 5, the air valve assembly still includes the discharge valve block, the setting is in the one end of valve plate 5 back to gleitbretter 3, be used for opening or close the second gas vent, the air valve assembly still includes lift stopper 6, the setting is in the one side of valve plate 5 back to gleitbretter 3, a extreme position for limiting the discharge valve block to open the second gas vent.
The first embodiment is as follows:
the structure comprises a cylinder 1, a piston 2, a sliding sheet 3 and an air valve assembly. Wherein, the pneumatic valve subassembly includes: a valve plate 5, an air suction valve plate 4, an air discharge valve plate, a lift limiter 6 and the like. The air valve assembly is fixed with the air cylinder 1 by pressing force generated by fixing pieces such as screws, jackscrews, wedge blocks and the like. Piston 2 links together through articulated mode with gleitbretter 3, and when gleitbretter 3 from 0 to 180, the volume between gleitbretter 3 and cylinder 1 and the valve block 4 of breathing in crescent, when gleitbretter 3 from 180 back-movements, the volume between gleitbretter 3 and cylinder 1 and the valve block 4 of breathing in reduces gradually. The movement process is equivalent to the air suction and exhaust process of the second independent working chamber. The conventional rotary compressor has certain height and width clearances for the piston 2, the sliding vane 3 and the cylinder 1: the height difference between the piston 2 and the sliding sheet 3 as moving parts and the cylinder 1 is a certain height difference, and when the height difference is larger, high-pressure gas and low-pressure gas are mixed; when the height difference is small, the piston 2 and the sliding sheet 3 have certain deformation under high temperature and high pressure, and although oil plays a role in lubrication, the risk of adhesion with the matching surface of the cylinder 1 still occurs.
With this construction, as with conventional rotary compressors, there are strict requirements on the fit clearance. In one embodiment:
height of the device: as shown in fig. 2: the height of the cylinder 1 is HA1, the height of the valve plate 5 is HB1, and the height of the air suction valve plate 4 is HC 1. The three satisfy the relation: 0 (HA1-HB1) is less than or equal to 45 mu m, and 0 (HA1-HC1) is less than or equal to 4 mm. The relation is as follows: 0 < (HA1-HB1) ≦ 45 μm, 0 < (HA1-HC1) ≦ 45 μm, namely the height of the cylinder 1 is greater than the height of the valve plate 5 within 45 μm, because the valve plate 5 cannot ensure the fit clearance between the upper and lower bearings and the cylinder 1 if being higher than the cylinder 1, resulting in the risk of leakage, and if the valve plate 5 is lower than the height of the cylinder 1, the second working chamber is communicated with the high back pressure gas in the shell, resulting in low performance. Relative to the fit clearance between the piston 2 and the sliding sheet 3 as moving parts and the cylinder 1, the valve plate 5 is a non-moving part, and the clearance between the valve plate and the cylinder 1 can be relatively larger while the sealing of the second working chamber is ensured. Similarly, the height of the suction valve plate 4 needs to satisfy the above relation. Preferably 0 < (HA1-HC1) ≦ 45 μm.
Thickness of the film: as shown in fig. 2: the thickness dimension SA2 of the tail end of the air valve assembly groove 15 of the air cylinder 1, the thickness dimension SA1 of the air valve assembly groove 15 and the thickness dimension SB1 of the valve plate 5 satisfy the following formula: SA2 is more than or equal to 1.5mm, and SA1 is more than SB1 and more than or equal to 3 mm. The size SA2 at the end of the valve assembly slot 15 of the cylinder 1 may be larger than zero, i.e. the valve assembly slot 15 is of a closed structure, or may be zero, and will be described with reference to another embodiment. The thickness size SA2 of the tail end of the air valve assembly groove 15 of the air cylinder 1 meets the relation: SA2 is larger than or equal to 1.5mm, and if the size SA2 of the tail end of the air valve assembly groove 15 is shorter, on one hand, the strength of the tail end cannot be ensured, and the tail end is insufficient in strength to cause deformation after machining, so that the phenomena of flatness of the upper end surface and the lower end surface of the air cylinder 1, deformation of the slide sheet groove 14, deformation of the inner diameter of the air cylinder 1 and the like are caused. The above relation SA1 > SB1 is not less than 3mm because: valve plate 5 and sealed pipe and expansion pipe need satisfy certain cooperation distance in order to guarantee sealed length, if cooperation length is less than 3mm, then high-pressure gas link up with vice jar breathing pipe in the casing and lead to phenomenon such as performance low, vice jar intake pipe overheat.
The thickness dimension SA1 of the air valve assembly groove 15 of the air cylinder 1, the thickness dimension SB1 of the valve plate 5 and the thickness dimension SC1 of the air suction valve plate 4 need to satisfy the relation: SA1- (SB1+ SC1) is not less than 0.05mm and not more than 5mm, so that on one hand, the installation gap between the valve plate 5 and the air valve assembly groove 15 is ensured, and on the other hand, if the installation gap between the valve plate 5 and the air valve assembly groove 15 is too large, noise brought by airflow at the air valve assembly groove 15 is greatly influenced.
Length: as shown in fig. 3: when the size SA2 of the tail end of the air valve assembly groove 15 of the air cylinder 1 is not 0, the length of the air valve assembly groove 15 is LA1, and the length LB1 of the valve plate 5 satisfies the relation: LB1 is less than or equal to (LA1-0.05 mm). The relation is as follows: LB1 is less than or equal to (LA1-0.05) mm because the valve plate 5 needs to be mounted in the valve assembly groove 15.
Additionally, the minimum distance LA3 from the valve assembly slot 15 to the first intake port of the cylinder 1 satisfies the relationship: LA3 is more than or equal to 0.5 mm. As shown in fig. 4 and 5. LA3 is defined herein as the minimum distance from valve assembly slot 15 to the primary air intake, which may be the primary air intake in FIG. 5 or a trapezoidal primary air intake configuration. The reason for satisfying this relation is that when the closest distance from the air valve assembly groove 15 to the first air intake port of the air cylinder 1 is too small, the strength of the first air intake port of the air cylinder 1 is low, the first air intake port may be deformed after the tapered tube is pressed in, and then the high-pressure air in the casing enters the air intake chamber 17 to cause the phenomena of abnormal performance and the like.
Example two:
the valve assembly slot 15 is an open structure, i.e. when the size SA2 of the tail end of the valve assembly slot 15 of the cylinder 1 is 0. As shown in fig. 6, which is an assembly drawing of this embodiment, a side of the air valve assembly groove facing the air valve assembly is an open structure (i.e., the tail end of the air valve assembly groove is an open structure), and a side (side D) of the air valve assembly groove facing away from the first air intake port of the air valve assembly is an open structure.
The end face of the air valve assembly groove 15 can be processed by adopting a grinding mode on the end face of the air valve assembly groove 15 of the air cylinder 1 so as to ensure the precision of a matching surface. FIG. 7 is a sectional view in the direction of C-C in this embodiment.
In the height direction: as with the embodiments, the same dimensional requirements need to be met, and are not described in detail here.
In the thickness direction: the thickness dimension SA2 of the tail end of the air valve assembly groove 15 of the air cylinder 1 and the dimension SA1 of the air valve assembly groove 15 satisfy the following formula: SA1 is more than SB1 and more than or equal to 3mm, and SA1 is less than or equal to 0.05mm (SB1+ SC 1). Here, the width SA1 of the air valve assembly groove 15 means that the end face where the air valve assembly groove 15 is fitted is a starting point, and the length from the extension line of the other end face of the valve plate 5 in the direction perpendicular to the end face where the air valve assembly groove 15 is fitted to the inner diameter of the main casing is a connection line, preferably, the valve plate is rectangular and includes a first side 51, a second side 52, a third side and a fourth side connected in sequence, the first side and the third side extend in the length direction of the valve plate, the second side and the fourth side extend in the width direction of the valve plate, the first side is disposed near the sliding piece, the second side is disposed opposite to the first suction port, the intersection point M of the extension line of the second side and the end face of the air valve assembly facing the first side is a starting point, the second side extends, and extends in the direction of the second side to the inner diameter Q of the main casing, SA1 is. The three satisfy the above relation SA1 > SB1 ≥ 3mm because: valve plate 5 and sealed pipe and expansion pipe need satisfy certain cooperation distance in order to guarantee sealed length, if cooperation length is less than 3mm, then high-pressure gas link up with vice jar breathing pipe in the casing and lead to phenomenon such as performance low, vice jar intake pipe overheat. The relation is as follows: SA1- (SB1+ SC1) is not less than 0.05mm because it is necessary to ensure that the pump body part needs to ensure a clearance of at least 0.05mm with the inner diameter of the shell after assembly, so as to avoid the interference between the pump body and the shell.
In the length direction: as shown in fig. 8, when the valve assembly groove 15 of the cylinder 1 is of an open structure, the length of the valve assembly groove 15 is LA1, and the length LB1 of the valve plate 5 satisfies the relationship: LA1 is more than or equal to 0.5LB1 and less than or equal to 2LB1mm, namely: the length LA1 of the air valve assembly slot 15 can be greater than the length LB1 of the valve plate 5, or less than the length of the air valve assembly slot 15. LA1 is less than or equal to 2LB1mm, which can ensure a larger matching surface, reduce the deformation of the matching end surface, and the like, and ensure enough sealing distance, but the finish machining surface is not too large, and the cost is reduced. The reason why LA1 is not less than 0.5LB1 is to ensure a sufficient sealing distance between the cylinder 1, the valve plate 5 and the suction valve plate 4.
Additionally, the minimum distance LA3 from the valve assembly slot 15 to the first intake port of the cylinder 1 satisfies the relationship: LA3 is more than or equal to 0.5 mm. LA3 is defined herein as the minimum distance from valve assembly groove 15 to the primary air intake, which may be the primary air intake of FIG. 5 or may be a trapezoidal primary air intake configuration. The reason for satisfying this relation is that when the closest distance from the air valve assembly groove 15 to the first air intake port of the air cylinder 1 is too small, the strength of the first air intake port of the air cylinder 1 is low, the first air intake port may be deformed after the tapered tube is pressed in, and then the high-pressure air in the casing enters the air intake chamber 17 to cause the phenomena of abnormal performance and the like.
Example three:
the air valve assembly groove 15 is an open structure, and is different from the second embodiment in that one side of the air valve assembly groove facing the air valve assembly is an open structure, that is, when the tail end of the air valve assembly groove 15 of the air cylinder 1 is an open structure, as shown in fig. 9, an assembly drawing of the second embodiment is shown.
Length and height direction: as with the embodiments, the same dimensional requirements need to be met, and are not described in detail here.
In the thickness direction: the same size requirements as in the second embodiment need to be satisfied, and are not described herein again.
Additionally, the minimum distance LA3 from the valve assembly slot 15 to the first intake port of the cylinder 1 satisfies the relationship: LA3 is more than or equal to 0.5 mm. LA3 is defined herein as the minimum distance from valve assembly groove 15 to the primary air intake, which may be the primary air intake of FIG. 5 or may be a trapezoidal primary air intake configuration. The reason for satisfying this relation is that when the closest distance from the air valve assembly groove 15 to the first air intake port of the air cylinder 1 is too small, the strength of the first air intake port of the air cylinder 1 is low, the first air intake port may be deformed after the tapered tube is pressed in, and then the high-pressure air in the casing enters the air intake chamber 17 to cause the phenomena of abnormal performance and the like.
In summary, the compression mechanism according to the embodiment of the invention not only provides the second working chamber for compressing gas by using the sliding vane, but also provides the valve assembly groove for installing the valve assembly, thereby providing a feasible structural scheme for the normal operation of the second working chamber. The manufacturing is simple, the installation is reliable, and the requirement of high cost performance can be met.
According to the compression mechanism provided by the embodiment of the invention, the size of each key part of the second working cavity and the mutual matching size relation are provided, so that the second working cavity can meet the performance requirement, and higher working efficiency is ensured.
In the description of the present invention, the term "plurality" means two or more unless explicitly specified or limited otherwise; the terms "connected," "secured," and the like are to be construed broadly and unless otherwise stated or indicated, and for example, "connected" may be a fixed connection, a removable connection, an integral connection, or an electrical connection; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description of the present specification, it is to be understood that the terms "upper", "lower", "front", "rear", "left", "right", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the referred device or unit must have a specific direction, be configured and operated in a specific orientation, and thus, should not be construed as limiting the present invention.
In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (17)

1. A compressor, comprising:
a cylinder having a first working chamber, a slide groove, and a valve assembly groove, the first working chamber having a first intake port and a first exhaust port;
the piston is eccentrically and rotatably arranged in the first working cavity;
the sliding sheet can be arranged in the sliding sheet groove in a reciprocating motion mode, and the front end of the sliding sheet is abutted against the piston;
the air valve assembly is arranged in the air valve assembly groove, a second working cavity is defined by the air valve assembly, the sliding sheet and the sliding sheet groove, the air valve assembly comprises a valve plate, and the valve plate is provided with a second air suction port and a second air exhaust port which are communicated with the second working cavity;
wherein the height of the cylinder is HA1, the height of the valve plate is HB1, and the value is more than 0 (HA1-HB1) and less than or equal to 45 mu m.
2. The compressor of claim 1,
the air valve assembly comprises an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, and the height of the air suction valve plate is HC1, and is less than 0 (HA1-HC1) and less than or equal to 4 mm.
3. The compressor of claim 2,
0＜(HA1-HC1)≤45μm。
4. compressor according to any one of claims 1 to 3,
the tail end of the air valve assembly groove is of a non-open structure, the thickness of the tail end of the air valve assembly groove is SA2, and SA2 is more than or equal to 1.5 mm; and/or the tail end of the air valve assembly groove is of a non-open structure, the thickness of the valve plate is SB1, the thickness of the air valve assembly groove is SA1, and SA1 is greater than SB1 and is larger than or equal to 3 mm.
5. Compressor according to any one of claims 1 to 3,
the tail end of the air valve assembly groove is of a non-open structure, the thickness of the air valve assembly groove is SA1, the thickness of the valve plate is SB1, the air valve assembly comprises an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, the thickness of the air suction valve plate is SC1, and then SA1- (SB1+ SC1) is not more than 0.05mm and not more than 5 mm.
6. Compressor according to any one of claims 1 to 3,
the tail end of the air valve assembly groove is of a non-open structure, the length of the air valve assembly groove is LA1, the length of the valve plate is LB1, and LB1 is less than or equal to (LA1-0.05 mm).
7. Compressor according to any one of claims 1 to 3,
the tail end of the air valve assembly groove is of a non-open structure, the length of the valve plate is LB1, the air valve assembly comprises an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, the width of the air suction valve plate is LC1, and LC1 is not more than LB 1.
8. Compressor according to any one of claims 1 to 3,
the air valve assembly groove is of an open structure.
9. The compressor of claim 8,
one side of the air valve assembly groove facing the air valve assembly is of an open structure; and/or one side of the air valve assembly groove, which faces the air valve assembly and is back to the first air suction port, is of an open structure.
10. The compressor of claim 9,
one side of the air valve assembly groove facing the air valve assembly is of an open structure, and the air valve assembly groove facing the tail end of the air valve assembly is processed in a grinding mode; and/or one side of the air valve assembly groove, which faces the air valve assembly and is back to the first air suction port, is of an open structure, and the surface of the air valve assembly groove, which faces the side of the air valve assembly, which is back to the first air suction port, is processed in a grinding mode.
11. The compressor of claim 8,
the thickness of the air valve assembly groove is SA1, the thickness of the valve plate is SB1, and SA1 is greater than SB1 and is larger than or equal to 3 mm.
12. The compressor of claim 11,
the air valve assembly comprises an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, the thickness of the air suction valve plate is SC1, and SA1- (SB1+ SC1) is not less than 0.05 mm.
13. The compressor of claim 9,
one side of the air valve assembly groove facing the air valve assembly is of an open structure, one side of the air valve assembly groove facing the air valve assembly and back to the first air suction port is of an open structure, the length of the air valve assembly groove is LA1, the length of the valve plate is LB1, and then LA1 is more than or equal to 0.5LB1 and less than or equal to 2LB 1.
14. The compressor of claim 9,
one side of the air valve assembly groove facing the air valve assembly is of an open structure, the length of the air valve assembly groove is LA1, the length of the valve plate is LB1, and LB1 is not more than (LA1-0.05 mm).
15. The compressor of claim 9,
one side of the air valve assembly groove, which faces the air valve assembly, is of an open structure, the air valve assembly comprises an air suction valve plate arranged on the valve plate, the air suction valve plate is used for opening and closing the second air suction port, the width of the air suction valve plate is LC1, the length of the valve plate is LB1, and LC1 is not more than LB 1.
16. Compressor according to any one of claims 1 to 3,
the minimum distance from the air valve assembly groove to the first air suction port is LA3, and LA3 is more than or equal to 0.5 mm.
17. A refrigeration apparatus, characterized by comprising a compressor according to any one of claims 1 to 16.
CN201811504407.2A 2018-12-10 2018-12-10 Compressor and refrigeration equipment Active CN111287968B (en)

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08240189A (en) * 1995-03-03 1996-09-17 Toshiba Ave Corp Rotary compressor
JP2003097433A (en) * 2001-09-27 2003-04-03 Sanyo Electric Co Ltd Hermetic electric compressor
CN101344091A (en) * 2008-08-16 2009-01-14 广东美芝制冷设备有限公司 Coolant injection device and control method of rotary compressor
CN102230464A (en) * 2011-08-03 2011-11-02 中国电子科技集团公司第十六研究所 Axial suction and exhaust valve for linear compressor
CN108105091A (en) * 2018-02-02 2018-06-01 广东美芝制冷设备有限公司 Compression mechanism and with its compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH08240189A (en) * 1995-03-03 1996-09-17 Toshiba Ave Corp Rotary compressor
JP2003097433A (en) * 2001-09-27 2003-04-03 Sanyo Electric Co Ltd Hermetic electric compressor
CN101344091A (en) * 2008-08-16 2009-01-14 广东美芝制冷设备有限公司 Coolant injection device and control method of rotary compressor
CN102230464A (en) * 2011-08-03 2011-11-02 中国电子科技集团公司第十六研究所 Axial suction and exhaust valve for linear compressor
CN108105091A (en) * 2018-02-02 2018-06-01 广东美芝制冷设备有限公司 Compression mechanism and with its compressor

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