CN116928060A - Piston compressor and mobile refrigerator comprising same - Google Patents
Piston compressor and mobile refrigerator comprising same Download PDFInfo
- Publication number
- CN116928060A CN116928060A CN202210320381.6A CN202210320381A CN116928060A CN 116928060 A CN116928060 A CN 116928060A CN 202210320381 A CN202210320381 A CN 202210320381A CN 116928060 A CN116928060 A CN 116928060A
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- crankcase
- gas
- vent
- head
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- 238000004891 communication Methods 0.000 claims description 19
- 238000007599 discharging Methods 0.000 claims description 2
- 230000006835 compression Effects 0.000 description 7
- 238000007906 compression Methods 0.000 description 7
- 230000010349 pulsation Effects 0.000 description 7
- 230000000694 effects Effects 0.000 description 6
- 238000000034 method Methods 0.000 description 5
- 238000007789 sealing Methods 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
- F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
- F04B37/12—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use to obtain high pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/125—Cylinder heads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/128—Crankcases
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
- F25D19/003—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors with respect to movable containers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2201/00—Insulation
- F25D2201/30—Insulation with respect to sound
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compressor (AREA)
Abstract
The invention relates to a piston compressor, comprising a cylinder cover, a cylinder cover gasket, a valve plate, an air inlet valve, a valve gasket and a crankcase, wherein the cylinder cover comprises a cylinder cover high-pressure cavity and a cylinder cover exhaust hole, the crankcase comprises a crankcase high-pressure cavity and a crankcase exhaust hole corresponding to the cylinder cover exhaust hole, and the piston compressor is characterized by comprising a plurality of gas exhaust paths for exhausting gas entering the cylinder cover high-pressure cavity, wherein the plurality of gas exhaust paths comprise: one path of gas leaves from the high-pressure cavity of the cylinder cover and sequentially passes through the gas guide hole on the cylinder cover gasket, the gas guide hole on the valve plate, the gas guide hole on the gas inlet valve and the gas guide hole on the valve gasket to the crankcase channel so as to enter the high-pressure cavity of the crankcase, then enters the crankcase vent hole through the crankcase vent channel and then is discharged through the cylinder cover vent hole; and at least one other gas discharge path that exits from the head high pressure chamber and returns to be discharged through the head exhaust hole. In addition, the invention also relates to a mobile refrigerator.
Description
Technical Field
The present invention relates to a piston compressor, and more particularly, to a piston compressor having a plurality of gas discharge paths. Furthermore, the invention relates to a mobile refrigerator comprising such a piston compressor.
Background
Vibration and noise generated during operation of a piston compressor have been problems addressed by the industry, particularly in environments where noise is a high requirement. However, the piston compressor inevitably generates considerable vibration and loud noise due to the impact of high-pressure gas during the exhaust process.
For relatively large size and volume piston compressors, a large volume exhaust muffler is typically used to dampen vibration and reduce noise. However, for small/micro piston compressors, such as those used in mobile refrigerators (e.g., in-car refrigerators), such piston compressors still produce considerable shock vibration and loud noise when operated due to the size constraints on the volume of the exhaust muffler and the fact that the gas is always a single gas during the discharge.
Disclosure of Invention
The present invention aims to solve, at least to some extent, the above-described technical problems in the related art. To this end, a piston compressor is proposed, comprising a cylinder head, a cylinder head gasket, a valve plate, an inlet valve, a valve gasket and a crankcase, wherein the cylinder head comprises a cylinder head high pressure chamber and a cylinder head vent, and the crankcase comprises a crankcase passage, a crankcase high pressure chamber, a crankcase vent passage and a crankcase vent corresponding to the cylinder head vent, characterized in that the piston compressor has a plurality of gas discharge paths for discharging gas entering the cylinder head high pressure chamber, wherein the plurality of gas discharge paths comprises:
one path of gas leaves from the high-pressure cavity of the cylinder cover and sequentially passes through the gas guide hole on the cylinder cover gasket, the gas guide hole on the valve plate, the gas guide hole on the gas inlet valve and the gas guide hole on the valve gasket to the crankcase channel so as to enter the high-pressure cavity of the crankcase, then enters the crankcase vent hole through the crankcase vent channel and then is discharged through the cylinder cover vent hole; and
and at least one other gas discharge path which leaves from the high-pressure cavity of the cylinder cover and returns to be discharged through the cylinder cover exhaust hole.
The piston compressor according to the present invention provides an improved exhaust structure, i.e. with multiple gas discharge paths exiting from the head high pressure chamber and returning to be exhausted through the head exhaust port. The exhaust structure remarkably reduces gas pulsation by a counteracting effect formed by stroke differences among a plurality of gas exhaust paths, thereby reducing the vibration and noise of the whole machine when the piston compressor works.
According to one aspect of the invention, the crankcase passageway is a recess in communication with the crankcase high pressure chamber; and the crankcase vent passage is a recess with one end communicated with the crankcase high-pressure cavity and the other end communicated with the crankcase vent hole.
According to one aspect of the invention, the at least one additional gas vent path includes a gas vent path that exits from the head high pressure chamber through an additional gas vent in the head gasket, an additional gas vent in the valve plate, an additional gas vent in the intake valve, and an additional gas vent in the valve gasket in sequence to an additional crankcase passageway to enter the crankcase high pressure chamber, then through the crankcase vent passageway to the crankcase vent hole, and then through the head vent hole.
According to one aspect of the invention, the at least one additional gas discharge path includes a gas discharge path that exits from the head high pressure chamber to the additional crankcase vent passage to enter the crankcase vent hole and then be discharged through the head vent hole, in order, through an additional gas vent hole in the head gasket, an additional gas vent hole in the valve plate, an additional gas vent hole in the intake valve, and an additional gas vent hole in the valve gasket.
According to one aspect of the invention, the at least one additional gas discharge path includes a gas discharge path that exits from the head high pressure chamber through the additional gas vent on the head gasket, the additional gas vent on the valve plate, the additional gas vent on the intake valve, and the additional gas vent on the valve gasket in sequence to the additional crankcase passageway to enter the crankcase high pressure chamber, then through the crankcase vent passageway to the crankcase vent, and then through the head vent; and one path of gas leaves from the high-pressure cavity of the cylinder cover to the additional crankcase exhaust channel to enter the crankcase exhaust hole and then is exhausted through the cylinder cover exhaust hole through the other additional gas guide hole on the cylinder cover gasket, the other additional gas guide hole on the valve plate, the other additional gas guide hole on the air inlet valve and the other additional gas guide hole on the valve gasket.
According to one aspect of the invention, the additional crankcase passageway is a recess in communication with the crankcase high pressure chamber; and the additional crankcase vent passage is a recess in communication with the crankcase vent.
According to one aspect of the invention, the at least one additional gas discharge path includes two gas discharge paths that exit from the head plenum through additional gas vents in the head gasket, additional gas vents in the valve plate, additional gas vents in the intake valve, and additional gas vents in the valve gasket in sequence to the crankcase gas gallery, then into the crankcase plenum, then through the crankcase gas gallery into the crankcase vent, then out through the head vent, and into the crankcase vent, then out through the head vent, respectively.
According to one aspect of the invention, the crankcase gas gallery is in the form of an L-shaped recess, including a first pilot portion for directing gas to the crankcase high pressure chamber and a second pilot portion for directing gas to the crankcase vent.
According to one aspect of the invention, the at least one additional gas discharge path includes a gas discharge path that exits from the head high pressure chamber through an additional gas vent in the head gasket to a valve plate exhaust passage in the valve plate, then into a valve plate exhaust vent, and then out through the head exhaust vent.
According to one aspect of the invention, the valve plate exhaust passage is a through slit or recess in communication with the valve plate exhaust hole.
According to another aspect of the present invention there is also provided a mobile refrigerator comprising a piston compressor according to the above aspect, which may be, for example, a vehicle-mounted refrigerator.
Drawings
The invention will be further described with reference to the accompanying drawings and examples, in which:
FIG. 1A shows an exploded view of a first embodiment of a piston compressor according to the present invention having two gas discharge paths;
fig. 1B shows a schematic view of the gas flow profile in a first embodiment of a piston compressor according to the invention with two gas discharge paths;
FIG. 1C shows a schematic structural view of a crankcase in a first embodiment of a piston compressor according to the invention having two gas discharge paths;
fig. 2A shows an exploded view of a second embodiment of a piston compressor according to the invention with two gas discharge paths;
fig. 2B shows a schematic view of the gas flow profile in a second embodiment of a piston compressor according to the invention with two gas discharge paths;
fig. 2C shows a schematic structural view of a crankcase in a second embodiment of a piston compressor according to the invention with two gas discharge paths;
fig. 3A shows an exploded view of a third embodiment of a piston compressor according to the invention with two gas discharge paths;
fig. 3B shows a schematic view of the gas flow profile in a third embodiment of a piston compressor according to the invention with two gas discharge paths;
fig. 3C shows a schematic structural view of a valve plate in a third embodiment of a piston compressor according to the present invention having two gas discharge paths;
fig. 4A shows an exploded view of a first embodiment of a piston compressor according to the invention with three gas discharge paths;
fig. 4B shows a schematic view of the gas flow trend in a first embodiment of a piston compressor according to the invention with three gas discharge paths;
fig. 4C shows a schematic structural view of a crankcase in a first embodiment of a piston compressor according to the invention with three gas discharge paths;
FIG. 5A shows an exploded view of a second embodiment of a piston compressor according to the present invention having three gas discharge paths;
fig. 5B shows a schematic view of the gas flow trend in a second embodiment of a piston compressor according to the invention with three gas discharge paths;
fig. 5C shows a schematic structural view of a crankcase in a second embodiment of a piston compressor according to the invention with three gas discharge paths.
Detailed Description
Embodiments of the present invention are described in detail below, examples of which are illustrated in the accompanying drawings, wherein the same or similar reference numerals refer to the same or similar elements or elements having the same or similar functions. The embodiments described below by referring to the drawings are illustrative and intended to explain the present invention and should not be construed as limiting the invention.
First, fig. 1A, 2A, 3A, 4A and 5A schematically show main components of the piston compressor 100 and an assembly structure thereof. The piston compressor 100 includes a crankcase 1, a piston 2, a valve pad 3, an intake valve 4, a valve plate 5, a head pad 6, and a head 7; wherein the valve gasket 3 is arranged between the inlet valve 4 and the crankcase 1 for sealing between the inlet valve 4 and the crankcase 1, and the head gasket 6 is arranged between the head 7 and the valve plate 5 for sealing between the head 7 and the valve plate 5. As shown in fig. 1A, 2A, 3A, 4A and 5A, the crankcase 1 is provided with four screw holes 11, 12, 13, 14, which are located at substantially four corners of the crankcase end surface, for screw connection between the crankcase 1 and the valve plate 5 and the cylinder head 7, respectively, wherein the screw hole 13 is used for screw connection and also for gas passage (i.e., crankcase vent hole). The crankcase 1 is further provided with a compression chamber 15, in which compression chamber 15 the piston 2 is linearly reciprocated for compressing gas in the operating state of the compressor. The crankcase 1 is further provided with a crankcase high pressure chamber 16, which can be used for the discharge of gas to reduce pulsations during operation of the compressor. In addition, as shown in FIGS. 1B-1C, 2B-2C, 3B, 4B-4C and 5B-5C, a passage, namely a crankcase vent passage 17, is provided between the crankcase high pressure chamber 16 and the screw hole (i.e., crankcase vent hole) 13 to allow communication between the crankcase high pressure chamber 16 and the screw hole 13. The crankcase vent passage 17 is shown in the drawings in the form of a recess/groove, but it may also be in the form of a through hole in the wall of the screw hole 13, etc., as long as it communicates the screw hole 13 with the crankcase high pressure chamber 16. Also as can be seen in fig. 1B-1C, 2B-2C, 3B, 4B-4C and 5B-5C, the crankcase 1 is further provided with a crankcase channel 18 (which may for example be in the form of a recess/groove) extending substantially parallel to the edges of the crankcase 1. One end of the crankcase passage 18 communicates with the crankcase high pressure chamber 16, while the other end is in gaseous communication with an air vent 35 in the valve pad 3 in the assembled state. Referring to fig. 1A, 2A, 3A, 4A and 5A, the valve pad 3 functions to ensure a seal between the intake valve 4 and the crankcase 1 in the assembled state. Similarly to the end face of the crankcase 1, the valve pad 3 is provided with four screw holes 31, 32, 33, and 34, the positions of which correspond to the four screw holes 11, 12, 13, and 14 of the end face of the crankcase 1, respectively, wherein the screw hole 33 corresponding to the screw hole 13 serves as a valve pad exhaust hole. The intake valve 4 is provided with four screw holes 41, 42, 43, and 44, the positions of which correspond to the four screw holes 11, 12, 13, and 14 of the end face of the crankcase 1, respectively, wherein the screw hole 43 corresponding to the screw hole 13 serves as an intake valve exhaust hole. At the same time, the intake valve 4 is also provided with an air vent 45 in gaseous communication with the air vent 35. Further, as shown in fig. 1A, 2A, 3A, 4A and 5A, the valve plate 5 is also formed with four fixing screw holes 51, 52, 53 and 54, the positions of which correspond to the four screw holes 11, 12, 13 and 14 of the end face of the crankcase 1, respectively, wherein the fixing screw hole 53 corresponding to the screw hole 13 serves as a valve plate exhaust hole. The valve plate 5 is further provided with an air vent 55 in gaseous communication with the air vent 45. Meanwhile, the valve plate 5 is further fixed with an exhaust valve plate limiting plate 8 and an exhaust valve plate 9 at one end thereof, for example, by riveting, wherein the exhaust valve plate limiting plate 8 has the function of preventing the exhaust valve plate 9 from being excessively opened to generate plastic deformation so as to ensure the service life of the compressor. Referring to fig. 1A, 2A, 3A, 4A and 5A, the head gasket 6 functions to ensure sealing between the valve plate 5 and the head 7 in the assembled state; it is also formed with through holes 61, 62, 63 and 64 to correspond to the screw holes 11, 12, 13 and 14, respectively, for passing screws, in which the through hole 63 corresponding to the screw hole 13 serves as a head gasket exhaust hole, and also formed with one air vent hole 65 in gaseous communication with the air vent hole 55. Referring to fig. 1B, 2B, 3B, 4B and 5B, the head 7 may be made of, for example, aluminum, in which a head high pressure chamber 75 is defined, the head high pressure chamber 75 including a first portion 76, a second portion 77 and a third portion 78. The first portion 76 of the head plenum is in gaseous communication with the second and third portions 77, 78 via passages (e.g., in the form of notches 79) in the dividing wall. Wherein the second portion 77 of the head high pressure chamber 75 is in gaseous communication with the air guide holes 65 in the head gasket 6. Meanwhile, the cylinder head 7 includes four screw holes 71, 72, 73 and 74 corresponding to the screw holes 11, 12, 13 and 14, respectively, wherein the screw hole 73 corresponding to the screw hole 13 serves as a head exhaust hole.
Various embodiments of the multiple paths of exhaust gas in the exhaust structure in the operating state of the piston compressor according to the present invention will be described in detail below.
In a first embodiment having two gas discharge paths as shown in fig. 1A-1C, when the piston compressor is in operation, a motor (not shown) rotates to drive the piston 2 in a linear reciprocating motion within the compression chamber 15 to compress gas. When the gas reaches a certain pressure value, the gas pushes away the discharge plate 9, enters the head high pressure chamber 75, in particular the first part 76 of the head high pressure chamber, after which the gas enters the second part 77 and the third part 78, respectively, through the channel 79. The gas entering the second portion 77 leaves from the head high pressure chamber to enter the crankcase high pressure chamber 16, then enters the crankcase vent hole 13 through the crankcase vent passage 17, and then exits through the valve pad vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head pad vent hole 63, and the head cover vent hole 73 in this order, through one (first) gas vent hole 65 on the head gasket 6, one (first) gas vent hole 55 on the valve plate 5, one (first) gas vent hole 45 on the intake valve 4, and one (first) gas vent hole 35 on the valve pad 3, to form a first gas discharge path 101. The gas entering the third section 78 leaves from the head high pressure chamber and is discharged sequentially through the additional (second) gas vent 66 in the head gasket 6, the additional (second) gas vent 56 in the valve plate 5, the additional (second) gas vent 46 in the intake valve 4 and the additional (second) gas vent 36 in the valve gasket 3 to the additional crankcase passageway 19 to enter the crankcase high pressure chamber 16 and then through the crankcase vent passageway 17 to the crankcase vent hole 13 and then sequentially through the valve gasket vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head gasket vent hole 63 and the head vent hole 73, i.e., forms a second gas discharge path 102. In this process, the discharge gas is divided into two parts, and the stroke difference between the two different discharge paths forms a counteracting effect, so that the gas pulsation can be reduced, and vibration and noise during the operation of the compressor can be reduced. Wherein in embodiments the additional crankcase passage may take the form of a recess/groove similar to the crankcase passage, or alternatively any other form, as long as the additional crankcase passage is secured in communication with the crankcase high pressure chamber.
In a second embodiment having two gas discharge paths as shown in fig. 2A-2C, when the piston compressor is in operation, a motor (not shown) rotates to drive the piston 2 in a linear reciprocating motion within the compression chamber 15 to compress gas. When the gas reaches a certain pressure value, the gas pushes away the discharge plate 9, enters the head high pressure chamber 75, in particular the first part 76 of the head high pressure chamber, after which the gas enters the second part 77 and the third part 78, respectively, through the channel 79. The gas entering the second portion 77 leaves from the head high pressure chamber to enter the crankcase high pressure chamber 16, then enters the crankcase vent hole 13 through the crankcase vent passage 17, and then exits through the valve pad vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head pad vent hole 63, and the head cover vent hole 73 in this order, through one (first) gas vent hole 65 on the head gasket 6, one (first) gas vent hole 55 on the valve plate 5, one (first) gas vent hole 45 on the intake valve 4, and one (first) gas vent hole 35 on the valve pad 3, to form a first gas discharge path 101. The gas entering the third portion 78 exits from the head plenum through the additional (second) gas vent 66 in the head gasket 6, the additional (second) gas vent 56 in the valve plate 5, the additional (second) gas vent 46 in the intake valve 4, and the additional (second) gas vent 36 in the valve gasket 3 in sequence to the additional crankcase vent passage 171 to enter the crankcase vent hole 13 and then exits through the valve gasket vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head gasket vent hole 63, and the head vent hole 73 in sequence, i.e., to form the second gas vent path 102. In this process, the discharge gas is divided into two parts, and the stroke difference between the two different discharge paths forms a counteracting effect, so that the gas pulsation can be significantly reduced, and vibration and noise during the operation of the compressor can be further reduced. Wherein in this embodiment the additional crankcase vent passage may take the form of a recess/groove similar to the crankcase vent passage, or alternatively any other form, so long as the additional crankcase vent passage is secured in communication with the crankcase vent hole.
In addition or alternatively, in a third embodiment having two gas discharge paths as shown in fig. 3A-3C, when the piston compressor is operated, a motor (not shown) rotates to drive the piston 2 to reciprocate linearly within the compression chamber 15, thereby compressing gas. When the gas reaches a certain pressure value, the gas pushes away the discharge plate 9, enters the head high pressure chamber 75, in particular the first part 76 of the head high pressure chamber, after which the gas enters the second part 77 and the third part 78, respectively, through the channel 79. The gas entering the second portion 77 leaves from the head high pressure chamber to enter the crankcase high pressure chamber 16, then enters the crankcase vent hole 13 through the crankcase vent passage 17, and then exits through the valve pad vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head pad vent hole 63, and the head cover vent hole 73 in this order, through one (first) gas vent hole 65 on the head gasket 6, one (first) gas vent hole 55 on the valve plate 5, one (first) gas vent hole 45 on the intake valve 4, and one (first) gas vent hole 35 on the valve pad 3, to form a first gas discharge path 101. The gas entering the third portion 78 leaves the head high pressure chamber through the additional (second) gas guide holes 66 in the head gasket 6 to the valve plate exhaust passage 58 in the valve plate 5, then enters the valve plate exhaust hole 53, and then is exhausted through the head gasket exhaust hole 63 and the head exhaust hole 73 in sequence, i.e., forms a second gas exhaust path 102. The valve plate exhaust passage 58 may be a through slit communicating with the valve plate exhaust hole 63, as shown in fig. 3A to 3C, for example. It should be understood that other forms of valve plate exhaust passages, such as recesses/grooves formed in the end face of the valve plate facing the head gasket, are possible, provided that gas communication between the valve plate exhaust passages and the valve plate exhaust holes is ensured. In the discharge process of this embodiment, the discharge gas is divided into two parts, and the stroke difference between the two different discharge paths forms a canceling effect, so that the gas pulsation can be significantly reduced, and vibration and noise during operation of the compressor can be reduced. And the structure of forming a new exhaust passage on the valve plate can relatively simplify the structure of the compressor having a plurality of exhaust paths to some extent (since there is no need to provide additional/additional air guide holes and/or exhaust passages on the intake valve, valve pad and crankcase end surfaces).
Alternatively, the piston compressor according to the present invention may further have a discharge structure of three gas discharge paths. For example, in the first embodiment having three gas discharge paths as shown in fig. 4A to 4C, when the piston compressor is operated, a motor (not shown) rotates to drive the piston 2 to reciprocate linearly in the compression chamber 15, thereby compressing gas. When the gas reaches a certain pressure value, the gas pushes away the discharge plate 9, enters the head high pressure chamber 75, in particular the first part 76 of the head high pressure chamber, after which the gas enters the second part 77 and the third part 78, respectively, through the channel 79. The gas entering the second portion 77 leaves from the head high pressure chamber to enter the crankcase high pressure chamber 16, then enters the crankcase vent hole 13 through the crankcase vent passage 17, and then exits through the valve pad vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head pad vent hole 63, and the head cover vent hole 73 in this order, through one (first) gas vent hole 65 on the head gasket 6, one (first) gas vent hole 55 on the valve plate 5, one (first) gas vent hole 45 on the intake valve 4, and one (first) gas vent hole 35 on the valve pad 3, to form a first gas discharge path 101. The gas entering the third portion 78 of the head high pressure chamber exits from the head high pressure chamber and exits sequentially through the additional (second) gas vent 66 in the head gasket 6, the additional (second) gas vent 56 in the valve plate 5, the additional (second) gas vent 46 in the intake valve 4, and the additional (second) gas vent 36 in the valve gasket 3 to the additional crankcase passageway 19 to enter the crankcase high pressure chamber 16 and then through the crankcase vent passageway 17 to the crankcase vent hole 13 and then sequentially through the valve gasket vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head gasket vent hole 63, and the head vent hole 73 to form a second gas vent path 102. The gas that enters the third portion 78 of the head high pressure chamber leaves from the head high pressure chamber and is also discharged sequentially through the other additional (third) gas-guide hole 67 on the head gasket 6, the other additional (third) gas-guide hole 57 on the valve plate 5, the other additional (third) gas-guide hole 47 on the intake valve 4, and the other additional (third) gas-guide hole 37 on the valve gasket 3 to the additional crankcase gas discharge channel 171 to enter the crankcase gas discharge hole 13, and then sequentially passes through the valve gasket gas discharge hole 33, the intake valve gas discharge hole 43, the valve plate gas discharge hole 53, the head gasket gas discharge hole 63, and the head gas discharge hole 73, that is, to form a third gas discharge path 103. In this embodiment the crankcase 1 is formed with both an additional crankcase vent passage and an additional crankcase passage, which allows the vent gas to be divided into three parts, the difference of travel between the three different vent paths creating a further counteracting effect, whereby the gas pulsations and thus the vibrations and noise during operation of the compressor can be further reduced.
In addition or alternatively, in a second embodiment having three gas discharge paths as shown in fig. 5A-5C, when the piston compressor is operated, a motor (not shown) rotates to drive the piston 2 to reciprocate linearly within the compression chamber 15, thereby compressing gas. When the gas reaches a certain pressure value, the gas pushes away the discharge plate 9, enters the head high pressure chamber 75, in particular the first part 76 of the head high pressure chamber, after which the gas enters the second part 77 and the third part 78, respectively, through the channel 79. The gas entering the second portion 77 leaves from the head high pressure chamber to enter the crankcase high pressure chamber 16, then enters the crankcase vent hole 13 through the crankcase vent passage 17, and then exits through the valve pad vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head pad vent hole 63, and the head cover vent hole 73 in this order, through one (first) gas vent hole 65 on the head gasket 6, one (first) gas vent hole 55 on the valve plate 5, one (first) gas vent hole 45 on the intake valve 4, and one (first) gas vent hole 35 on the valve pad 3, to form a first gas discharge path 101. The gas entering the third portion 78 leaves from the head high pressure chamber and passes through the additional (second) gas vent 66 in the head gasket 6, the additional (second) gas vent 56 in the valve plate 5, the additional (second) gas vent 46 in the intake valve 4 and the additional (second) gas vent 36 in the valve gasket 3 in this order to the L-shaped crankcase gas guide channel 111 (specifically to the intersection of the two branches of the crankcase gas guide channel), then enters the crankcase high pressure chamber 16 via the first guide portion 112, then enters the crankcase vent hole 13 via the crankcase vent channel 17, and then exits through the valve gasket vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head gasket vent hole 63 and the head vent hole 73 in this order, respectively, thus forming a second gas vent path 102; and enters the crankcase vent hole 13 via the second guide portion 113 and then is discharged through the valve pad vent hole 33, the intake valve vent hole 43, the valve plate vent hole 53, the head gasket vent hole 63, and the head vent hole 73 in this order, that is, the third gas discharge path 103 is formed. In the process, the crankcase 1 comprises a crankcase gas guide channel with a first part and a second part which are communicated with a crankcase high-pressure cavity and a crankcase vent hole respectively at the end face of the crankcase, so that the exhaust gas can be divided into three parts, and the stroke difference between the three different exhaust paths forms a further counteracting effect, thereby further reducing gas pulsation and further reducing vibration and noise when the compressor works. In this embodiment, as shown in fig. 5A-5C, the crankcase gas gallery may be in the form of an L-shaped recess, for example, or alternatively take any other branched form, so long as communication with the crankcase high pressure chamber and crankcase vent is ensured.
It will be appreciated that the piston compressor with multiple gas discharge paths according to the present invention is highly advantageous for a size and space-constrained refrigeration apparatus, since the piston compressor according to the present invention is not affected by the increased size and space caused by the need to use a bulky exhaust muffler. According to yet another aspect of the invention, it relates to a mobile refrigerator, such as a vehicle-mounted refrigerator, comprising a piston compressor as defined according to any of the above embodiments. Due to the above-described advantages of the piston compressor, vibration and noise of the on-vehicle refrigerator including the same at the time of operation will be significantly reduced and reduced.
In the description of the present invention, it should be understood that the terms "upper", "lower", "inner", "outer", "side", and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, and are merely for convenience in describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation configuration and operation, and thus are not to be construed as limiting the present invention.
Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. Thus, a definition of "a first", "a second", "a third" feature may include one or more of the features, either explicitly or implicitly.
While embodiments of the present invention have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the invention, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the invention.
Claims (12)
1. A piston compressor comprising a cylinder head, a cylinder head gasket, a valve plate, an intake valve, a valve gasket, and a crankcase, wherein the cylinder head comprises a cylinder head high pressure chamber and a cylinder head vent, and the crankcase comprises a crankcase passage, a crankcase high pressure chamber, a crankcase vent passage, and a crankcase vent corresponding to the cylinder head vent, characterized in that the piston compressor has a plurality of gas discharge paths for discharging gas entering the cylinder head high pressure chamber, wherein the plurality of gas discharge paths comprises:
one path of gas leaves from the high-pressure cavity of the cylinder cover and sequentially passes through the gas guide hole on the cylinder cover gasket, the gas guide hole on the valve plate, the gas guide hole on the gas inlet valve and the gas guide hole on the valve gasket to the crankcase channel so as to enter the high-pressure cavity of the crankcase, then enters the crankcase vent hole through the crankcase vent channel and then is discharged through the cylinder cover vent hole; and
and at least one other gas discharge path which leaves from the high-pressure cavity of the cylinder cover and returns to be discharged through the cylinder cover exhaust hole.
2. The piston compressor of claim 1 wherein said crankcase passageway is a recess in communication with said crankcase high pressure chamber; and the crankcase vent passage is a recess with one end communicated with the crankcase high-pressure cavity and the other end communicated with the crankcase vent hole.
3. The piston compressor of claim 1 wherein the at least one additional gas discharge path includes a gas discharge path that exits from the head high pressure chamber through additional gas ports in the head gasket, additional gas ports in the valve plate, additional gas ports in the intake valve, and additional gas ports in the valve gasket in sequence to additional crankcase passages to enter the crankcase high pressure chamber and then through the crankcase vent passage to the crankcase vent and then to the head vent.
4. The piston compressor of claim 1 wherein the at least one additional gas discharge path comprises a gas discharge path that exits from the head plenum through additional gas ports in the head gasket, additional gas ports in the valve plate, additional gas ports in the intake valve, and additional gas ports in the valve gasket in sequence to additional crankcase vent passages to enter the crankcase vent and then exit through the head vent.
5. The piston compressor of claim 1 wherein the at least one additional gas discharge path includes a gas discharge path that exits from the head high pressure chamber through the additional gas port in the head gasket, the additional gas port in the valve plate, the additional gas port in the intake valve, and the additional gas port in the valve gasket in sequence to the additional crankcase passageway to enter the crankcase high pressure chamber and then enter the crankcase vent through the crankcase vent passageway and then exit through the head vent; and one path of gas leaves from the high-pressure cavity of the cylinder cover to the additional crankcase exhaust channel to enter the crankcase exhaust hole and then is exhausted through the cylinder cover exhaust hole through the other additional gas guide hole on the cylinder cover gasket, the other additional gas guide hole on the valve plate, the other additional gas guide hole on the air inlet valve and the other additional gas guide hole on the valve gasket.
6. The piston compressor of any one of claims 3-5, wherein the additional crankcase passageway is a recess in communication with the crankcase high pressure chamber; and the additional crankcase vent passage is a recess in communication with the crankcase vent.
7. The piston compressor of claim 1 wherein the at least one additional gas discharge path includes two gas discharge paths from the head plenum through the additional gas port in the head gasket, the additional gas port in the valve plate, the additional gas port in the intake valve and the additional gas port in the valve gasket in sequence to the crankcase gas gallery, then into the crankcase plenum, then through the crankcase gas gallery to the crankcase vent, then through the head vent, and then into the crankcase vent, and then through the head vent.
8. The piston compressor of claim 7 wherein the crankcase gas gallery is in the form of an L-shaped recess including a first pilot portion for directing gas to the crankcase high pressure chamber and a second pilot portion for directing gas to the crankcase vent.
9. The piston compressor of claim 1 wherein the at least one additional gas discharge path comprises a gas discharge path that exits the head plenum through additional gas ports in the head gasket to a valve plate exhaust passage in the valve plate and then into the valve plate exhaust port and then out through the head exhaust port.
10. The piston compressor of claim 9, wherein the valve plate exhaust passage is a through slit or recess in communication with the valve plate exhaust hole.
11. A mobile refrigerator, characterized in that it comprises a piston compressor according to any one of the preceding claims.
12. The mobile refrigerator of claim 11, wherein the mobile refrigerator is a vehicle-mounted refrigerator.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210320381.6A CN116928060A (en) | 2022-03-29 | 2022-03-29 | Piston compressor and mobile refrigerator comprising same |
| PCT/CN2023/084600 WO2023185906A1 (en) | 2022-03-29 | 2023-03-29 | Piston compressor and mobile refrigerator comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210320381.6A CN116928060A (en) | 2022-03-29 | 2022-03-29 | Piston compressor and mobile refrigerator comprising same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116928060A true CN116928060A (en) | 2023-10-24 |
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ID=88199287
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210320381.6A Pending CN116928060A (en) | 2022-03-29 | 2022-03-29 | Piston compressor and mobile refrigerator comprising same |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN116928060A (en) |
| WO (1) | WO2023185906A1 (en) |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0886279A (en) * | 1994-09-16 | 1996-04-02 | Toyota Autom Loom Works Ltd | Reciprocating type compressor |
| CN101876309B (en) * | 2010-07-30 | 2012-10-31 | 思科普压缩机(天津)有限公司 | Exhaust structure and piston compressor comprising same |
| CN201818464U (en) * | 2010-07-30 | 2011-05-04 | 丹佛斯制冷设备(天津)有限公司 | Exhaust structure and piston compressor provided with same |
| CN206738123U (en) * | 2017-05-24 | 2017-12-12 | 安徽美芝制冷设备有限公司 | The compression mechanism and reciprocating compressor of reciprocating compressor |
| CN110761969A (en) * | 2018-07-26 | 2020-02-07 | 安徽美芝制冷设备有限公司 | Reciprocating compressor and refrigerating apparatus |
| CN113266551A (en) * | 2021-06-21 | 2021-08-17 | 浙江冰峰压缩机有限公司 | Piston compressor with embedded valve plate |
-
2022
- 2022-03-29 CN CN202210320381.6A patent/CN116928060A/en active Pending
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2023
- 2023-03-29 WO PCT/CN2023/084600 patent/WO2023185906A1/en unknown
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| WO2023185906A1 (en) | 2023-10-05 |
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