JP2014234768A - Hermetic type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hermetic type compressor with low noise at low cost.SOLUTION: A side wall configuring a resonance type silencer has an uneven shape, the resonance type silencer is made to be a multistage Helmholtz type silencer, and a side branch type silencer is configured connected to a refrigerant passage. Components such as a sealed container for configuring a hermetic type compressor and air column (space) inside the sealed container are vibrated, resonance is generated at the natural vibration frequency (resonance frequency), and the increase in noise of the hermetic type compressor can be effectively suppressed.

Description

  The present invention relates to a hermetic compressor used in a refrigeration cycle such as a refrigerator-freezer.

  As a hermetic compressor used in a refrigeration cycle such as a refrigerator-freezer, the opening of a compression chamber composed of a cylinder and a piston is sealed with a valve plate having a suction valve and a discharge valve, and the piston reciprocates and sucks. Some have a compression action by opening and closing valves and discharge valves.

  In such a hermetic compressor, the energy of pressure pulsation accompanying the opening and closing of the suction valve vibrates parts such as the hermetic container and the air column (space) in the hermetic compressor, thereby causing natural vibration. There is a problem that resonance occurs at a number (resonance frequency) and noise of the hermetic compressor increases.

  For the purpose of solving the problem, a tail tube whose one end opens into the sealed container and guides the refrigerant gas in the sealed container and the other end is an outlet, an expansion chamber in which the outlet of the tail tube opens, one end There is known a hermetic compressor including a suction muffler having an inlet of the expansion chamber and a communication pipe having an outlet at the other end communicating with a suction valve (for example, see Patent Document 1).

  FIG. 4 is a cross-sectional view of a hermetic compressor disclosed in Patent Document 1. As shown in FIG. FIG. 5 is a sectional view of the suction muffler of the hermetic compressor.

  As shown in FIGS. 4 and 5, the hermetic compressor disclosed in Patent Document 1 includes a hermetic container 1, a compression chamber 7 including a cylinder 3 and a piston 5, and a piston 5 of the compression chamber 7. A valve plate 13 having a suction valve 11 for sealing the opening end 9 on the opposite side and a discharge valve (not shown), and a suction muffler 15 communicating with the suction valve 11 of the valve plate 13. .

  One end of the suction muffler 15 opens into the sealed container 1, a tail pipe inlet 17 that guides a refrigerant gas (not shown) inside the sealed container 1, and the other end is a tail pipe outlet 19, and a tail pipe outlet 19. The expansion chamber 23 is opened, and the communication tube inlet 25 at one end is opened to the expansion chamber 23 and the communication tube outlet 27 at the other end is connected to the suction valve 11.

  As a result, in the hermetic compressor disclosed in Patent Document 1, due to the energy of pressure pulsation accompanying opening and closing of the suction valve 11, components such as the hermetic container 1 and the air in the hermetic container 1 are formed. The column (space) is vibrated, resonating at the natural frequency (resonance frequency), and an increase in noise of the hermetic compressor can be suppressed.

JP 2005-180413 A

However, in the conventional hermetic compressor, since the silencing mechanism of the suction muffler 15 is an expansion silencer using the expansion chamber 23, its characteristics are effective for reducing noise in a wide range of frequencies. The reduction effect is small, and since it is an expansion type, there is a problem that the body of the suction muffler becomes large.

  The present invention solves the above-mentioned conventional problems, and by efficiently arranging a plurality of Helmholtz type and side branch type resonance silencers inside the body of the suction muffler, the noise reduction effect is high, and An object of the present invention is to provide a hermetic compressor with low noise and low cost by using a compact suction muffler.

  In order to solve the conventional problems, a hermetic compressor according to the present invention includes an electric element including a stator and a rotor, a compression element driven by the electric element, the electric element, and the compression element. An airtight container in which lubricating oil is stored, and the compression element includes a cylindrical cylinder block, a piston that reciprocates in an inner space of the cylinder block, and a side of the cylinder block opposite to the piston. A valve plate having a suction valve and a discharge valve for sealing the opening portion of the valve, and a suction muffler having one end opened in the internal space of the sealed container and the other end communicating with the suction valve of the valve plate. The suction muffler has a plurality of resonance silencers that share the front and rear walls with the body inside the substantially rectangular parallelepiped body.

  As a result, the energy of pressure pulsation accompanying the opening and closing of the intake valve vibrates parts such as the sealed container and the air column (space) in the sealed container and resonates at the natural frequency (resonant frequency). It can raise | generate and it can suppress effectively that the noise of a hermetic type compressor increases.

  Further, by configuring the resonance silencer, the suction muffler body can be made compact.

  According to the hermetic compressor of the present invention, the suction muffler has a plurality of resonance type silencers sharing the front and rear walls with the body inside the substantially rectangular parallelepiped body, and is associated with opening and closing of the suction valve. The energy of the pressure pulsation causes the components such as the sealed container constituting the hermetic compressor and the air column (space) in the hermetic container to vibrate, causing resonance at the natural frequency (resonance frequency), and the noise of the hermetic compressor The increase can be effectively suppressed, and it is compact. Therefore, it is possible to provide a hermetic compressor that is quiet in sound, compact and inexpensive.

Sectional drawing of the side surface of the hermetic compressor which concerns on this Embodiment 1. Front sectional view of the suction muffler of the hermetic compressor shown in FIG. Side view of the suction muffler of the hermetic compressor shown in FIG. Sectional drawing of the side surface of the hermetic compressor disclosed in Patent Document 1 Front sectional view of the suction muffler of the hermetic compressor shown in FIG.

  The first invention includes an electric element including a stator and a rotor, a compression element driven by the electric element, a sealed container in which the electric element and the compression element are stored, and lubricating oil is stored. The compression element includes a cylindrical cylinder block, a piston that reciprocates in the internal space of the cylinder block, a suction valve and a discharge valve that seal an opening of the cylinder block opposite to the piston. And a suction muffler having one end opened to the internal space of the sealed container and the other end communicating with the suction valve of the valve plate, and is disposed inside a substantially rectangular parallelepiped body of the suction muffler. Has a plurality of resonant silencers that share the front wall and the rear wall with the vessel.

  As a result, the energy of pressure pulsation accompanying the opening and closing of the intake valve vibrates parts such as the sealed container and the air column (space) in the sealed container and resonates at the natural frequency (resonant frequency). It can raise | generate and it can suppress effectively that the noise of a hermetic type compressor increases.

  Further, by configuring the resonance silencer, the suction muffler body can be made compact and the cost can be reduced.

  Further, according to a second invention, in the first invention, a refrigerant passage is formed in the interior of the body by the inner wall of the suction muffler body, the outer wall of the resonance silencer, and the front and rear walls of the body. .

  Thereby, a smooth flow of refrigerant gas can be obtained.

  Further, according to a third invention, in the second invention, the side wall constituting the resonance silencer has an uneven shape, and the resonance silencer is a multistage Helmholtz silencer and connected to the refrigerant passage. A side branch type silencer is constructed.

  Thereby, a plurality of noises of any frequency can be effectively attenuated.

  In a fourth aspect based on the third aspect, the resonance frequency of the multi-stage Helmholtz silencer is in the range of 400 to 700 Hz in the refrigerant atmosphere used.

  As a result, the air column (space) in the hermetic container is vibrated and resonates at the natural frequency (resonance frequency), and the increase in noise of the hermetic compressor can be effectively suppressed.

  In a fifth aspect based on the third aspect, the resonance frequency of the side branch type silencer connected to the refrigerant passage is in the range of 1500 to 5000 Hz in the refrigerant atmosphere used.

  As a result, it is possible to effectively suppress an increase in noise of the hermetic compressor due to vibration of components such as a hermetic container constituting the hermetic compressor and resonance at the natural frequency (resonance frequency).

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a side sectional view of the hermetic compressor according to the first embodiment. 2 is a front sectional view of the suction muffler of the hermetic compressor shown in FIG. FIG. 3 is a side view of the suction muffler of the hermetic compressor shown in FIG.

  First, the configuration of the hermetic compressor will be described.

  As shown in FIGS. 1 to 3, the hermetic compressor 100 according to the first embodiment includes a hermetic container 101. The closed vessel 101 is provided with a suction pipe 103 so as to penetrate the wall of the closed vessel 101. The suction pipe 103 is configured such that a refrigerant gas (not shown) supplied from a refrigerant cycle (not shown) flows and is supplied into the sealed container 101.

  A lubricating oil 105 is stored at the bottom of the sealed container 101. Further, the sealed container 101 includes a compression element 107 for sucking and compressing the refrigerant gas, and an electric element 113 including a rotor 109 and a stator 111 for driving the compression element 107. A compressor main body 115 is supported via an elastic body 117 such as a spring.

  The compression element 107 includes a crank pin 119 and a cylinder block 121. The crank pin 119 is formed so as to be eccentric to the crank shaft 123 press-fitted and fixed to the rotor 109. The crankshaft 123 is disposed so that the shaft center extends in the vertical direction, and is rotatably held by the bearing 125. An oil supply pipe 127 whose part is immersed in the lubricating oil 105 and whose upstream end is open in the lubricating oil 105 is press-fitted and fixed to the lower end portion of the crank pin 119.

  The cylinder block 121 is arranged so that its axis extends in the horizontal direction, and is formed in a substantially cylindrical shape. The piston 129 is reciprocally inserted into the cylinder block 121. A cylindrical piston pin 131 is fixed to the piston 129. The piston pin 131 is connected to the crank pin 119 by a connecting rod 133.

  A valve plate 135 is provided on the opening end surface on the top dead center side of the cylinder block 121 so as to seal the opening end surface. A cylinder head 137 that forms a high-pressure chamber (not shown) is fixed to the valve plate 135 so as to cover the valve plate 135.

  The valve plate 135 includes a suction valve 139, a discharge valve, and a discharge valve seat that communicate with the internal space of the cylinder block 121 and the internal space of the sealed container 101 by opening and closing the valve plate 135. A discharge valve (not shown) communicating with the high pressure chamber is provided.

  A compression chamber 141 is formed by the cylinder block 121, the valve plate 135, and the end face of the piston 129 on the valve plate 135 side.

  A suction muffler 143 is connected to the suction valve 139 of the valve plate 135.

  The suction muffler 143 has a tail tube inlet 145 having one end opened to the internal space of the sealed container 101 and a tail tube outlet 153 having the other end opened to a substantially rectangular parallelepiped body 147 internal space 149 of the suction muffler 143. A communication pipe 159 having a communication pipe inlet 155 having one end opened to the internal space 149 of the suction muffler 143 and a communication pipe outlet 157 having the other end connected to the suction valve 139; and a body 147 of the suction muffler 143 Are a resonance type silencer 167 which is a multistage Helmholtz type silencer 165 sharing the front wall 161 and the rear wall 163 of the body 147, and an inner wall 169 of the body 147 of the suction muffler 143 and the resonance type noise reduction. Refrigerant passages 173a and 173b formed in the interior of the vessel 147 by the outer wall 171 of the vessel 167, the front wall 161 and the rear wall 163 of the vessel 147, and a multistage helix Side-branch silencers 175a, 175b, 175c, 175d, 175e, and 175f connected to refrigerant passages 173a and 173b formed by the convex and concave outer wall 171 of the resonance silencer 167, which is a Holtz silencer 165. .

  At this time, the resonance type silencer 167 which is a multi-stage Helmholtz type silencer 165 and the side branch type silencers 175a, 175b, 175c, 175d, 175e, 175f have respective opening directions equal to or less than the horizontal direction. The lubricating oil 105 does not stay in the silencer during transportation or operation of the hermetic compressor.

  Next, the operation of the hermetic compressor 100 will be described with reference to FIGS.

First, when the crankshaft 123 is rotationally driven by the rotation of the rotor 109 of the electric element 113, the eccentric (turning) motion of the crankpin 119 is converted into a linear reciprocating motion by the connecting rod 133, and the piston 129 is moved. The cylinder block 121 is reciprocated to perform a predetermined suction operation (suction stroke) and compression operation (compression stroke).

  At this time, the oil supply pipe 127 attached to the tip of the crank pin 119 pumps up the lubricating oil 105 by the centrifugal pump effect as it rotates in the lubricating oil 105. The lubricating oil 105 pumped into the oil supply pipe 127 is supplied to each sliding portion.

  A refrigerant gas (not shown) supplied from the refrigerant cycle flows through the suction pipe 103 attached so as to penetrate the wall portion of the sealed container 101, and is sucked into the suction muffler 143 from the tail pipe inlet 145.

  Refrigerant gas (not shown) sucked into the suction muffler 143 is supplied from the suction valve 139 to the compression chamber 141 through the communication pipe inlet 155, the communication pipe 159, and the communication pipe outlet 157 through the refrigerant passages 173a and 173b. And compressed by a piston 129 that reciprocates in the cylinder block 121 and discharged from a discharge valve (not shown).

  At this time, the energy of the pulsation generated by the opening / closing operation of the suction valve 139 propagates in a reverse flow from the suction valve 139 to the suction muffler 143, and is released from the tail tube inlet 145 to the sealed container 101.

  However, in the hermetic compressor 100 according to the first embodiment, inside the suction muffler 143, the energy of this pulsation is converted into a multistage Helmholtz silencer 165 and a plurality of side branch silencers 175a, 175b, 175c, 175d, Due to the effects of 175e and 175f, after being greatly attenuated in various frequency bands, the tail tube inlet 145 opens to the sealed container 101.

  Next, the effect of the hermetic compressor 100 will be described with reference to FIGS.

  As described above, in the hermetic compressor 100 according to the first embodiment, the suction muffler 143 has a tail pipe inlet 145 whose one end opens into the internal space of the sealed container 101 and the other end that is a substantially rectangular parallelepiped of the suction muffler 143. A tail tube 153 having a tail tube outlet 151 opened to the inner space 149 of the vessel body 147, a communication pipe inlet 155 opened at one end to the vessel 147 inner space 149 of the suction muffler 143, and the other end communicated with the suction valve 139. A plurality of resonances having a communication pipe 159 having a communication pipe outlet 157 and a front wall 161 and a rear wall 163 of the container body 147 in the interior of the container body 147 of the suction muffler 143 and having an opening downward from the horizontal direction. A mold silencer 167.

  As a result, compared to the hermetic compressor disclosed in Patent Document 1, the pulsating energy generated by the opening / closing operation of the suction valve 139 is greatly attenuated by the plurality of resonance silencers 167 inside the suction muffler 143. Then, the air is released from the tail tube inlet 145 to the sealed container 101, so that the components such as the sealed container 101 constituting the hermetic compressor 100 and the air column (space) in the sealed container 101 are vibrated to cause natural vibration. It is possible to effectively suppress an increase in noise of the hermetic compressor by causing resonance at a number (resonance frequency). In addition, since the opening direction of the resonance silencer 167 is lower than the horizontal direction, the lubricating oil 105 does not stay inside, and the resonance frequency of the resonance silencer 167 and the effect of attenuation of the pulsation energy are stable.

  Furthermore, it is possible to design the suction muffler more compactly compared to an expansion silencer that requires a large capacity to obtain a noise attenuation effect, and the cost is low.

In the hermetic compressor 100 according to the first embodiment, the inner wall 169 of the container 147 of the suction muffler 143, the outer wall 171 of the resonance silencer 167, the front wall 161 of the container 147, and the rear wall 163 Thus, the refrigerant passages 173a and 173b are formed inside the container body 147.

  As a result, the flow of the refrigerant gas inside the suction muffler 143 is smoother and the efficiency of the hermetic compressor is better than that of the hermetic compressor disclosed in Patent Document 1.

  Further, in the hermetic compressor 100 according to the first embodiment, the side wall constituting the resonance silencer 167 has an uneven shape, and the resonance silencer 167 is a multistage Helmholtz silencer 165 and a refrigerant. Side branch type silencers 175a, 175b, 175c, 175d, 175e, 175f having openings downward from the horizontal direction connected to the passages 173a, 173b are configured.

  As a result, as compared with the hermetic compressor disclosed in Patent Document 1, the energy of pulsation caused by the opening / closing operation of the suction valve 139 becomes a multistage Helmholtz silencer 165 inside the suction muffler 143. After being greatly attenuated in various frequency bands by side branch type silencers 175a, 175b, 175c, 175d, 175e, 175f connected to the refrigerant passages 173a, 173b, the tail pipe inlet 145 is opened to the sealed container 101. Therefore, components such as the sealed container 101 constituting the hermetic compressor 100 and air columns (spaces) in the hermetic container 101 are vibrated, causing resonance at the natural frequency (resonance frequency), and noise of the hermetic compressor Can be effectively suppressed. Further, since the opening direction of the resonance type silencer 167 and the side branch type silencers 175a, 175b, 175c, 175d, 175e, 175f is downward from the horizontal direction, the lubricating oil 105 does not stay inside, The resonance frequency of the resonance type silencer 167 and the side branch type silencers 175a, 175b, 175c, 175d, 175e, and 175f and the attenuation effect of pulsation energy caused thereby are stable.

  In the hermetic compressor 100 according to the first embodiment, the resonance frequency of the multistage Helmholtz silencer 165 is set to 400 to 700 Hz.

  As a result, compared to the hermetic compressor disclosed in Patent Document 1, the air column (space) in the hermetic container 101 is vibrated and resonates at the natural frequency (resonant frequency). The increase in noise can be effectively suppressed.

  In the hermetic compressor 100 according to the first embodiment, the resonance frequencies of the side branch type silencers 175a, 175b, 175c, 175d, 175e, and 175f connected to the refrigerant passages 173a and 173b are set to 1500 to 5000 Hz. .

  Thereby, compared with the hermetic compressor disclosed in Patent Document 1, parts such as the hermetic container 101 constituting the hermetic compressor 100 are vibrated and resonate at a natural frequency (resonance frequency). An increase in the noise of the hermetic compressor can be effectively suppressed.

  From the above description, many modifications and other embodiments of the present invention are obvious to one skilled in the art.

  Accordingly, the foregoing description should be construed as illustrative only and is provided for the purpose of teaching those skilled in the art the best mode of carrying out the invention.

  The details of the structure and / or function may be substantially changed without departing from the spirit of the invention.

  The hermetic compressor according to the present invention improves the noise attenuation effect of the suction muffler, and the components such as the hermetic container and the air column in the hermetic container constituting the hermetic compressor by the energy of pressure pulsation accompanying opening and closing of the suction valve. Because (space) is vibrated and resonates at the natural frequency (resonance frequency), it is possible to effectively suppress the increase in noise of the hermetic compressor, and the sound is quiet and compact. Is useful.

DESCRIPTION OF SYMBOLS 101 Airtight container 105 Lubricating oil 107 Compression element 109 Rotor 111 Stator 113 Electric element 121 Cylinder block 129 Piston 135 Valve plate 139 Suction valve 143 Suction muffler 147 Body 161 Front wall 163 Rear wall 165 Helmholtz type silencer 167 Resonance type silencer 169 Inner side wall 171 Outer side wall 173a, 173b Refrigerant passage 175a, 175b, 175c, 175d, 175e, 175f Side branch type silencer

Claims (5)

An electric element comprising a stator and a rotor;
A compression element driven by the electric element;
A closed container in which the electric element and the compression element are accommodated and in which lubricating oil is stored, and the compression element includes a cylindrical cylinder block;
A piston that reciprocates in the internal space of the cylinder block;
A valve plate having a suction valve and a discharge valve for sealing the opening of the cylinder block opposite to the piston;
A suction muffler having one end opened to the internal space of the sealed container and the other end communicating with the suction valve of the valve plate;
A hermetic compressor having a plurality of resonant silencers sharing a front wall and a rear wall with the container inside a substantially rectangular container of the suction muffler. 2. The sealed type according to claim 1, wherein a refrigerant passage is formed in the interior of the container by the inner wall of the container body of the suction muffler, the outer wall of the resonance silencer, the front wall and the rear wall of the container body. Compressor. The side wall of the resonance type silencer has an uneven shape, and the resonance type silencer is a multi-stage Helmholtz type silencer and a side branch type silencer connected to the refrigerant passage. 2. The hermetic compressor according to 2. The hermetic compressor according to claim 3, wherein a resonance frequency of the multistage Helmholtz silencer is in a range of 400 to 700 Hz in a refrigerant atmosphere used. The hermetic compressor according to claim 3, wherein a resonance frequency of the side branch silencer connected to the refrigerant passage is in a range of 1500 to 5000 Hz in a refrigerant atmosphere used.