Electrically-operated sealed compressor

Electrically operated hermetic compressor

The present invention generally relates to a relatively compact compressor, such as the freezer compartment of a household refrigerator or display box, and in detail, it relates to the valve mechanism or air extraction system of such a compressor.

In recent years, the valve mechanism in the compressor has been improved in many ways to increase the efficiency of the compressor. However, the demand from the market is not only to increase the efficiency of the compressor, but also to suppress the noise emitted from the compressor.

The early technology of the compressor valve mechanism is disclosed in, for example, Japanese Patent Early Publication (Unexamined) No. 3-175174.

Hereinafter, referring to Figures 24, 25, and 26, the compressor valve mechanism disclosed in the Japanese Patent Early Publication No. 3-175174 mentioned above will be discussed.

Figure 24 is a cross-sectional view of the valve mechanism of the early technology in an assembled state along the horizontal direction, Figure 25 is a longitudinal cross-sectional view of Figure 24, and Figure 26 is an exploded view of the valve mechanism of the early technology. In Figures 24 to 26, reference numeral 1 represents a valve mechanism, and reference numeral 4 represents a valve plate with two exhaust ports 2 and two exhaust ports 3 defined therein, one of which selectively opens and closes the exhaust port 3 The exhaust reed valve 22 is fixed in a recess 21 defined by the valve plate 4. Reference numeral 23 represents that the stopper is fixed to the valve plate by rivets 24 as the lifting height adjustment of the reed valve 22. The suction reed valve 11, the flat gasket 12, the valve plate 4, the front gasket 13 and the cylinder head 14 are all latched to the cylinder 10.

The cylinder 10 contains a piston drivingly coupled with an electric motor (not shown) for axial reciprocating movement within the cylinder 10. The cylinder head 14 has an exhaust chamber 25 defined therein together with the valve plate 4 And an exhaust chamber 26.

The operation of the early technology compressor valve mechanism constructed as described above will now be described here.

Due to the reciprocating movement of the piston 15, the refrigerant gas in the suction chamber 25 flows through the suction port 2 in the valve plate 4 during the opening of the suction reed valve 11, and is drawn into the cylinder 10, and then in the exhaust spring. While the fin valve 22 is open, the refrigerant gas is compressed in the cylinder 10 before the refrigerant gas is discharged to the exhaust chamber in the cylinder head 14 through the exhaust port 3.

However, in the early technology of the valve mechanism discussed above, because the refrigerant gas flows through the two exhaust ports 3 at the same time and is discharged into the exhaust chamber 26, the refrigerant gas flows interfere with each other and hinder the smooth flow of the refrigerant gas. Reduce exhaust efficiency and compressor performance. In addition, because the refrigerant gas is simultaneously discharged from the two exhaust ports 3 into the exhaust chamber 26 intermittently, unnecessarily large pulses and noise are generated.

At the same time, when the refrigerant gas is separately discharged from the two exhaust ports 3 and the exhaust reed valve 22 is pushed at the same time, the exhaust reed valve has only a unique resonance frequency (tone), therefore, 3000 revolutions at 50 Hz and It is difficult to properly resonate the reed valve 22 and optimize the exhaust efficiency in the case of 3600 revolutions at 60 Hz. Furthermore, even if the number of revolutions of the compressor changes like a frequency converter, there is still a problem that the change in the number of revolutions results in a considerable reduction in efficiency.

In addition, since the exhaust reed valve 22 has only one resonance tone, there is another problem in that the hissing sound generated by the individual flows of the refrigerant gas discharged from the two exhaust outlets tends to be interfered and increased, thereby generating considerable The noise.

In addition, the exhaust reed valve 22 is fixed in the groove 21 by the stopper 23 and rivets, which requires some complicated equipment and inefficient assembly.

Japanese Patent Publication (Unexamined) No. 6-74786 discloses an air extraction system for an electrically-operated hermetic compressor, in which a muffler with a number of compartments separated from each other is used for sound attenuation. However, there is a problem here in that if the effect of silencing is prioritized, the suction efficiency of the belt clip is reduced due to reduced performance.

Also, because pumping represents an intermittent flow formed as a result of the selective opening or closing of a reed valve, the flow inertia of the refrigerant gas cannot be fully utilized and the load capacity on the cylinder tends to be reduced. This trend is strengthened when the noise reduction performance of the muffler increases.

The hermetic compressor requires that the muffler's silencing performance and its suction efficiency be improved.

The present invention has been developed to overcome the aforementioned shortcomings.

Therefore, an object of the present invention is to provide an improved electric-operated hermetic compressor, which has high exhaust efficiency and the noise generated as a result of interference of refrigerant gas exhaust is at a low level to complete noise suppression, and the refrigerant gas The pulse is very small.

Another object of the present invention is to provide an electrically operated hermetic compressor capable of adjusting the change of the number of revolutions.

A further object of the present invention is to provide an electrically operated hermetic compressor in which the discharge valve can be easily installed to facilitate assembly.

Another object of the present invention is to provide an electrically operated hermetic compressor in which the stopper and the discharge valve can be easily fixed in position.

Still another objective of the present invention is to provide an electrically operated hermetic compressor that can improve and maintain the muffler with respect to the compression performance of the compressor even if the load of the cylinder increases, without reducing the flow inertia of the refrigerant gas, Therefore, the performance of noise cancellation is increased.

In order to achieve the above and other objectives, an electrically operated hermetic compressor according to the present invention includes a cylinder, a cylinder head, which is mounted on the cylinder and has an exhaust chamber defined therein and a first And the second exhaust chamber, a piston contained in the cylinder, and a valve mechanism. The valve mechanism includes an exhaust muffler and a valve plate. The valve plate has at least one exhaust port defined therein, the first and second exhaust ports defined therein, and the first exhaust port defined therein. One and the second pass through the hole. The first exhaust port and the first through hole are in communication with the first exhaust chamber, while the second exhaust port and the second through hole are in communication with the second exhaust chamber. The valve mechanism also includes first and second exhaust valves arranged on the valve plate and respectively contained in the first and second exhaust chambers. An exhaust gasket with a reed valve for selectively opening and closing the exhaust port, an exhaust gasket for sealing the valve plate and the cylinder head, and an exhaust muffler. The first and second exhaust chambers are separated from each other by exhaust gaskets to form separate spaces, and the first and second through holes are communicated with the exhaust muffler.

This structure eliminates the interference of the refrigerant gas flow (so far this interference is caused by the refrigerant gas being introduced into a single exhaust chamber through the two exhaust holes at the same time), thus avoiding the reduction of exhaust efficiency.

Advantageously, the first and second exhaust chambers have different volumes. Therefore, the pulse frequencies in the first and second exhaust chambers are different. This prevents the refrigerant gas from flowing into the exhaust muffler at the same pulse frequency. May cause an increase in resonance noise.

It is also advantageous that the first and second passage holes have different diameters. Because of this method, the refrigerant gas flow flows through the first and second passage holes at different speeds. Therefore, when it enters the exhaust muffler, the refrigerant gas flow has different pulse frequencies, which can avoid the same pulse of the refrigerant gas flow. The frequency flowing into the exhaust muffler may cause an increase in resonance noise.

The cylinder head may have a mixing chamber defined therein, and the valve plate may have a through hole defined therein to allow the mixing chamber to communicate with the exhaust muffler. In this case, the first and second rows The air chamber is substantially separated from the mixing chamber by an exhaust gasket, but the first and second exhaust chambers communicate with the mixing chamber through first and second communication holes defined in the cylinder head.

This structure avoids the reduction in exhaust efficiency caused by the interference of the refrigerant gas flow intermittently passing through the two exhaust ports so far. In addition, because the function of the mixing chamber can be reduced and the refrigerant gas flow to the exhaust muffler can be corrected, the pulse of the refrigerant gas is quite small and the refrigerant gas flow is stable, so that the noise generation can be reduced considerably.

In another form of the present invention, an electrically operated hermetic compressor includes a cylinder, and a cylinder head disposed on the cylinder has an exhaust chamber defined therein and an exhaust chamber defined therein, and one is accommodated in the cylinder The piston inside, and a valve mechanism. The valve mechanism includes a valve plate having at least one suction port defined therein and first and second exhaust ports defined therein. The blowing port faces the exhaust chamber, while the first and second exhaust ports face the exhaust chamber. The valve mechanism also includes first and second exhaust valves arranged on the valve plate and contained in the exhaust chamber to selectively open and close the first and second exhaust ports, and a suction spring with a reed valve The sheet faces the exhaust port to selectively open or close the exhaust port. The first and second exhaust valves are connected at the end of a valve and form a whole. The first and second exhaust valves are fixed on the valve plate, and the end of the valve is firmly fixed on the valve plate.

The above-mentioned structure facilitates the assembly of the exhaust valve to the respective positions of the corresponding combined exhaust port, and is also accompanied by a good usable property.

Advantageously, the first and second exhaust valves have different lengths or have different widths as measured from the end of the valve. This structure shows good exhaust efficiency and minimizes the interference noise of refrigerant gas. More specifically, the first and second exhaust valves have different oscillation frequencies. Therefore, when the refrigerant gas flows through the first and second exhaust valves, the first and second exhaust valves show different resonances ( The refrigerant gas has a corresponding resonance under different rotation times), while preventing the increase of hiss that may be caused by mutual interference.

The electrically-operated hermetic compressor may include first and second stoppers arranged on the valve plate to adjust the rising height of the first and second exhaust valves, respectively. The first and second stoppers are connected at the end of one stopper and are integrally formed as a whole. The first and second exhaust valves are fixed on the valve plate, and the end of the valve is firmly fixed on the valve plate by the end of the stopper. Due to this configuration, the two exhaust valves and the two stoppers can be easily fixed in their proper positions.

Advantageously, the first and second stoppers have different oblique angles measured from a bend at the end of the stopper, or the first and second exhaust valves have different oblique angles measured from a bend at the end of the stopper. Different lengths of the free end of the stopper. Due to this structure, the first and second exhaust valves can easily have different rising heights, and from the viewpoint of having different rising heights, when the refrigerant gas flows through the first and second exhaust valves, the first It operates differently from the second exhaust valve, so that the exhaust efficiency is appropriate and the noise caused by mutual interference is also minimized.

Each of the first and second stoppers can have a different length of the reserved part as the pressure exhaust valve combined with it. This structure has an effect in that the effective valve length of the first exhaust valve and the effective valve length of the second exhaust valve can be easily made to have different values, and when the refrigerant gas passes through the first and second exhaust valves, The first and second exhaust valves exhibit different resonances (the refrigerant gas has corresponding resonances at different rotation times), and at the same time prevents the increase of hissing noise that may be caused by mutual interference.

The valve plate may have a groove defined therein for accommodating the first and second exhaust valves. In this case, the first and second exhaust valves are fixed on the valve plate, and the end of the valve is firmly fixed on the valve plate by allowing the end of the stopper to be press-fitted in the groove. This structure has an effect in that the exhaust valve can be easily fixed by press-fitting the end of the stopper in the groove. In addition, the fixed part that is press-fitted in the groove can be easily formed as the first and second A partition in the exhaust chamber.

In a further form of the present invention, an electrically operated hermetic compressor includes a hermetic box, components of the compressor (contained in the hermetic box and containing an electric motor, a cylinder, a piston, and a crankshaft), and one is contained in the hermetic box The suction muffler in the inside, one is arranged on one of the components of the compressor and has a defined suction port valve plate in it, a reed valve selectively opens or closes the suction port, and one extends from the suction port to The passage of the suction muffler is a refrigerant flow branch pipe whose opening enters a part of the passage to allow the suction gas to flow into and out of here.

The structure described above has such a function that during the period when the reed valve is closed, the flow inertia in the suction passage is retained by the refrigerant flow branch pipe, but during the period when the reed valve is opened, the refrigerant accumulated by the refrigerant flow branch pipe The gas flows into the cylinder to maintain the flow inertia of the sucked gas, thus maintaining and improving the charging efficiency of the refrigerant gas into the cylinder.

The refrigerant flow branch pipe can be contained in the exhaust silencer. In addition to the function of maintaining the flow inertia of the sucked refrigerant gas, this structure also has the function of simplifying the structure.

In addition, a refrigerant flow branch pipe can be provided to improve an optimal pumping efficiency according to the number of revolutions. According to this structure, during the period when the reed valve is selectively opened and closed, the flow rate of refrigerant gas flowing into or out of the refrigerant flow branch pipe can be resonated by a gas column created in the refrigerant flow branch pipe according to the number of revolutions of the compressor. Improve, thereby maintaining and improving the charging efficiency of the refrigerant gas entering the cylinder under a specific number of revolutions.

Preferably, the refrigerant flow branch pipe has an opening located near the suction port. This structure has the function of enabling the flow inertia to be maintained near the suction port, thereby maintaining and improving the efficiency of refrigerant gas charging into the cylinder.

More preferably, the suction muffler has a refrigerant gas suction port with a cross-sectional area smaller than the suction port. According to this structure, while maintaining the efficiency of the refrigerant gas charging into the cylinder, the silencing performance of the muffler can be improved by the refrigerant flow branch pipe.

In another form of the present invention, an electrically-operated hermetic compressor includes a hermetic box, compressor components (contained in the hermetic box and having an electric motor, a cylinder, a piston, and a crankshaft), one contained in The suction muffler in the sealed box has a valve plate which is arranged on one of the compressor elements and has a suction port defined therein, a reed valve selectively opens and closes the suction port, and one from The suction port extends to the passage of the suction muffler, and a sealed chamber, so formed to enter the passage through a branch pipe to allow the suction gas to flow into and out of here.

Another sealed chamber may be formed to enter the channel through another gas flow branch pipe to allow the inhaled gas to flow into and out of here.

The airtight chamber can be contained in the exhaust silencer.

Advantageously, the sealed cell opens into the channel near the suction port.

Preferably, the suction muffler has an introduction port defined therein, and the introduction port has a smaller cross-sectional area than the suction port.

According to the above-mentioned structure, when the reed valve is opened during the pumping stroke, gas flows into the cylinder, and during the subsequent compression stroke, the reed valve is closed. At this time, the internal pressure leading from the inside of the muffler to the suction port in the passage is increased due to the rapid interruption of the flow. The gas that increases the internal pressure is contained in the sealed chamber via the branch pipe. According to this, the flow inertia can be maintained. Then, during the pumping stroke, the accumulated gas immediately flows into the cylinder to promote a smooth and stable suction flow, while avoiding the reduction of flow inertia.

<p>1Valve Machinery</p><p>2(two) suction port</p><p>3(two) exhaust ports</p><p>4Valve plate</p><p>10Cylinder</p><p>11Suction reed valve</p><p>12Flat liner</p><p>13Front (head) liner</p><p>14Cylinder head</p><p>15Piston</p><p>21Concave (groove)</p><p>22Exhaust reed valve</p><p>23Stopper</p><p>24Riveting (hinge) nail</p><p>25Exhaust Chamber</p><p>26Exhaust Chamber</p><p>101Piston</p><p>102Cylinder</p><p>103Muffler</p><p>104Muffler inlet</p><p>105Inhalation pad</p><p>106Suction reed</p><p>107Reed valve</p><p>108Valve plate</p><p>110Two suction ports</p><p>111First exhaust port</p><p>112First exhaust valve</p><p>112aFirst through hole</p><p>112bFirst through hole</p><p>113Second exhaust port</p><p>114Second exhaust valve</p><p>114aSecond through hole</p><p>114bSecond through hole</p><p>115Fixed parts</p><p>116Exhaust Gasket</p><p>117Cylinder head</p><p>118Suction Chamber</p><p>119First exhaust chamber</p><p>119bFirst exhaust chamber</p><p>120Second Exhaust Chamber</p><p>120bSecond exhaust chamber</p><p>121Exhaust silencer</p><p>122First exhaust chamber</p><p>123Second Exhaust Chamber</p><p>125First connecting hole</p><p>126Second connecting hole</p><p>127Mixed</p><p>128Through hole</p><p>200Screw</p><p>201Piston</p><p>202Cylinder</p><p>203Muffler</p><p>204Muffler inlet</p><p>205Inhalation pad</p><p>206Suction reed</p><p>207Reed valve</p><p>208Valve plate</p><p>210Two suction ports</p><p>211First exhaust port</p><p>211aFirst exhaust valve</p><p>211bFirst exhaust valve</p><p>212First exhaust valve</p><p>213Second exhaust port</p><p>213aSecond exhaust valve</p><p>213bSecond exhaust valve</p><p>214Second exhaust valve</p><p>214athrough hole</p><p>214bvalve end</p><p>215screw</p><p>216Exhaust Gasket</p><p>217Cylinder head</p><p>218Suction Chamber</p><p>219Exhaust Chamber</p><p>221Exhaust silencer</p><p>321First exhaust valve</p><p>322Second exhaust valve</p><p>323valve end</p><p>324First stop</p><p>325Second stop</p><p>326End of stopper</p><p>327Locating pin</p><p>328First exhaust port</p><p>329Second exhaust port</p><p>331First exhaust valve</p><p>332Second exhaust valve</p><p>333valve end</p><p>334First stop</p><p>335Second stop</p><p>336End of stopper</p><p>337Bending part</p><p>338First stop (free) (front) end</p><p>339Second stopper (free) (front) end</p><p>341First exhaust valve</p><p>342Second exhaust valve</p><p>342aEnd of stopper</p><p>343Bending part</p><p>344First stop (free) end</p><p>345Second stopper (free) end</p><p>346First stop</p><p>347Second stop</p><p>351First exhaust valve</p><p>351aFirst stop</p><p>352Second exhaust valve</p><p>352aSecond stopper</p><p>353 (of the first stopper) reserved part</p><p>354(Second stopper) reserved part</p><p>355(First) Effective valve position</p><p>356(Second) Effective valve position</p><p>401Valve plate</p><p>402Groove</p><p>403First exhaust port</p><p>404Second exhaust port</p><p>405First exhaust valve</p><p>405aSecond exhaust valve</p><p>406valve end</p><p>407First stop</p><p>408Second stop</p><p>409End of stopper</p><p>410Fixed part</p><p>411Cylinder head</p><p>412Suction Chamber</p><p>413First exhaust chamber</p><p>414Second Exhaust Chamber</p><p>501Power-operated hermetic compressor</p><p>502Sealed Box</p><p>503Compressor components</p><p>504Electric Motor</p><p>505Compressor Unit</p><p>506Spring</p><p>507Cylinder block</p><p>508Bearing</p><p>509Axle</p><p>510Centrifugal part</p><p>511Connecting rod</p><p>512Piston</p><p>513Valve plate</p><p>514Suction port (and exhaust port)</p><p>515Reed valve</p><p>516Cylinder head</p><p>517Suction Silencer</p><p>518Access tube</p><p>519Refrigerant flow branch pipe</p><p>519'Opening part</p><p>520Inlet</p><p>521Suction tube</p><p>522Refrigerant flow branch pipe</p><p>523Refrigerant flow branch pipe</p><p>524Refrigerant flow branch pipe</p><p>525Refrigerant flow branch pipe</p><p>525'Opening part</p><p>530Sealed Chamber</p><p>533Sealed Chamber</p><p>534Refrigerant flow branch pipe</p><p>535Refrigerant flow branch pipe</p><p>536Sealed Chamber</p><p>537Sealed Chamber</p><p>538Sealed Chamber</p><p>539Refrigerant flow branch pipe</p>

The above and other objectives and features of the present invention will become more apparent from the description of the following preferred embodiments and with reference to the accompanying drawings. Similar reference numerals are used to denote similar parts from beginning to end, and among them: No. 1 Figure is an exploded perspective view of a compressor valve mechanism according to the first embodiment of the present invention; Figure 2 is a cross-sectional view of an important part of the valve mechanism of Figure 1; Figure 3 is a diagram similar to Figure 2 , But depicts one of its improvements; Figure 4 is a diagram similar to Figure 2, but depicts another improvement; Figure 5 is a diagram similar to Figure 2, but depicts its further improvement; Figure 6 is an exploded perspective view of a compressor valve mechanism according to the second embodiment of the present invention; Figure 7 is a cross-sectional view along the line VIII-VIII in Figure 6; Figure 8 is similar to the first Figure 7 is a diagram, but depicts an improvement about it; Figure 9 is a diagram similar to Figure 7, but depicts another improvement; Figure 10 is similar to Figure 6 Figure, but depicts an improvement about it; Figure 11 is an external view of an important part of the valve mechanism; Figure 12 is an illustration similar to Figure 11, but depicts an improvement about it ; Figure 13 is a diagram similar to Figure 11, but depicts another improvement about it; Figure 14 is a diagram similar to Figure 6, but depicts another improvement about it; Figure 15 is a cross-sectional view of an electrically operated hermetic compressor according to the third embodiment of the present invention; Figure 16 is a cross-sectional view along the line XVI-XVI in Figure 15; Figure 17 is similar to the first Figure 16 is a diagram, but depicts an improvement about it; Figure 18 is a diagram similar to Figure 16, but depicts another improvement; Figure 19 is similar to Figure 16 Fig. 20 is a diagram similar to Fig. 16, but in accordance with the fourth embodiment of the present invention; Fig. 21 is a diagram similar to Fig. 20, but depicts Figure 22 is a diagram similar to Figure 20, but depicts another improvement about it; Figure 23 is a diagram similar to Figure 20, but depicts it Figure 24 is a cross-sectional view of an important part of a traditional compressor valve mechanism; Figure 25 is another cross-sectional view of an important part of the traditional compressor valve mechanism of Figure 24; and Figure 26 is an exploded perspective view of important parts of the conventional compressor valve mechanism shown in Figure 24.

Hereinafter, several embodiments of the present invention will be described with reference to the accompanying drawings.

(First embodiment)

Fig. 1 is an exploded perspective view of the valve mechanism of the compressor according to the first embodiment of the present invention, and Fig. 2 is a cross-sectional view of the important part of the valve mechanism as seen from the arrow A in Fig. 1.

The reference numeral 101 in the first and second figures represents a piston, which is operable to compress the refrigerant gas into the space in the cylinder 102 when it reciprocates in the cylinder 102. Reference numeral 103 represents a muffler having a muffler introduction port 104 fixed therein for pumping refrigerant gas.

Reference numeral 105 represents an inhalation pad, and reference numeral 106 represents an inhalation reed having a reed valve 107. Reference numeral 108 represents a valve plate with two suction ports 110 fixed therein and aligned with the reed valve 107. In addition, the valve plate 108 includes a first exhaust port 111, a first exhaust valve 112 to selectively open and close the first exhaust port 111, a first through hole 112a, a second exhaust port 113, and a The second exhaust valve 114 selectively opens and closes the second exhaust port 113 and the second through hole 114a. The first and second exhaust valves 112 and 114 are firmly fixed to the valve plate 108 by a fixing member 115.

Reference numeral 116 represents an exhaust gas gasket between the valve plate 108 and the cylinder head 117. Due to the sealing effect of the exhaust gasket 116, an exhaust chamber 118 communicating with the suction port 110 and a first and second exhaust chambers 119 and 120 respectively communicating with the exhaust ports 111 and 113 are formed. The first exhaust chamber 119 accommodates the first exhaust valve 112 and communicates with the first through hole 112a, while the second exhaust chamber 120 accommodates the second exhaust valve 113 and communicates with the second through hole 114a. Both of the first and second passage holes 112a and 114a communicate with the exhaust muffler 121.

The operation and effect of the compressor valve mechanism constructed as described above will be discussed here.

As a result of the reciprocating movement of the piston 101, the refrigerant gas is guided from the muffler introduction port 104 through the suction muffler 103 into the suction chamber 118 and then from the suction port 110 by the effect of selectively opening and closing the reed valve 107 Draw into the cylinder 102.

After the refrigerant gas compressed in the cylinder 102 has flowed through the first and second exhaust ports 111 and 113, it is exhausted by the effect of selectively opening and closing the first and second exhaust valves 112 and 114. Enter the first and second exhaust chambers 119 and 120. Because the first and second exhaust chambers 119 and 120 are formed separately, the refrigerant gas flow generated by the exhaust does not interfere with each other around the first and second exhaust valves 112 and 114, so the refrigerant gas flow is smooth Stably flows through the first and second exhaust ports 111 and 113. In summary, the reduction in exhaust efficiency can be avoided. Up to now, it is caused by an interference between one airflow surrounding the first exhaust valve 112 and another airflow surrounding the second exhaust valve 114 of.

The compressor of the present invention described so far includes a piston 101, a cylinder 102 accommodating the piston 101, a reed valve 107 to selectively open and close a suction muffler 103 and a suction port 110, one having two Exhaust ports 111 and 113 and two valve plates 108 passing through holes 112a and 114a, two exhaust valves 112 and 114 installed on the valve plate 108, one with a suction chamber 118 and two exhaust chambers 119 and 120 The cylinder head 117, an exhaust gasket 116 as a sealing valve plate 108 and the cylinder head 117, and an exhaust muffler 121. The first exhaust chamber 119 accommodates the first exhaust valve 112 and communicates with the first exhaust port 111 and the first through hole 112a, while the second exhaust chamber 120 accommodates the second exhaust valve 114 and communicates with the second exhaust valve 114 The port 113 communicates with the second through hole 114a. In addition, the first and second exhaust chambers 119 and 120 are completely isolated from each other by the exhaust gasket 116 to form separate spaces. At the same time, the first and second through holes 112a and 114a communicate with the exhaust muffler 121 . This structure eliminates the interference of the refrigerated gas flow (up to now it is caused by the refrigerated gas being introduced into a single exhaust chamber through two exhaust holes at the same time), thus avoiding the reduction of exhaust efficiency.

As shown in Figure 3, the first and second exhaust chambers 122 and 123 may have different volumes, which are different from the embodiment shown in Figures 1 and 2.

In the above structure, by the effect of selectively opening and closing the first and second exhaust valves 112 and 114, the refrigerant gas is discharged into the first and second exhaust through the first and second exhaust ports 111 and 113 Room 122 and 123.

It is worth noting here that the intermittent exhaust of the refrigerated gas tends to generate an undesirable pressure pulse in the exhaust chamber, just as the relatively large pulse of the pulse source causes oscillation or increased noise. However, according to the present invention, because the first and second exhaust chambers 122 and 123 have different volumes and therefore have different pulse frequencies, the refrigerant gas passes through the first and second passage holes 112a and 112a at different pulse frequencies. 114a flows into the exhaust muffler 121 so as to avoid increasing the noise that may be caused by a resonance of the refrigerant gas flowing into the exhaust muffler at the same pulse frequency. In addition, by appropriately determining the volume of the first and second exhaust chambers 122 and 123, the pulse in the exhaust muffler can be reduced considerably.

As shown in Fig. 4, the first and second through holes 112b and 114b may have different diameters.

With the above structure, with the effect of selectively opening and closing the first and second exhaust valves 112 and 114, the refrigerant gas is discharged into the first and second rows through the first and second exhaust ports 111 and 113 Air chambers 122 and 123. After that, the refrigerant gas in the first and second exhaust chambers 122 and 123 is discharged into the exhaust muffler 121 through the first and second passage holes 112b and 114b. Because the two passing holes 112b and 114b have different diameters, the refrigerant gas flows through at different speeds. As a result, the refrigerant gas flow has different pulse frequencies when entering the exhaust muffler 121, so that noise increase caused by a resonance of the refrigerant gas flow entering the exhaust muffler with the same pulse frequency can be avoided.

As shown in Figure 5, the cylinder head 117 may have a mixing chamber 127 fixed therein, which communicates with the first and second exhaust chambers 119b and 120b via the first and second communication holes 125 and 126, respectively. . The mixing chamber 127 also communicates with the exhaust muffler 127 via a through hole 128.

With the above-mentioned structure, the refrigerant gas is discharged into the first and second exhausts through the first and second exhaust ports 111 and 113 through the selective opening and closing of the first and second exhaust valves 112 and 114. Chambers 119b and 120b. Because the first and second exhaust chambers 119b and 120b are isolated from each other, the refrigerant gas discharged therein will not interfere with each other, so the exhaust efficiency will not be reduced. After being throttled by the first and second communication holes 125 and 126, the refrigerant gas in the first and second exhaust chambers 119b and 120b is then guided into the mixing chamber 127. Because the exhaust of refrigerated gas is performed intermittently, they generate pulsation. However, since the refrigerating gas is throttled by the first and second communication holes 125 and 126, such a pulse is quite small. Furthermore, the mixing chamber 127 serves as a space for relaxing the intermittent air flow 121 flowing into the exhaust muffler through the passage hole 128. Therefore, the pulse in the exhaust muffler 121 is reduced and the refrigerated gas flows smoothly, so that the generation of noise is reduced considerably.

It must be noted that although in the above embodiment, the valve plate 108 is described as having two suction ports 110, it may only have one suction port.

(Second embodiment)

Hereinafter, the second embodiment of the present invention will be described with reference to FIGS. 6 to 14.

Fig. 6 is an exploded view of a compressor valve mechanism according to the second embodiment of the present invention, and Fig. 7 is a cross-sectional view of an important part taken along the line VII-VII of Fig. 6.

In Figs. 6 and 7, reference numeral 201 represents a piston, which is operable to compress the refrigerated gas into the space in the cylinder 202 when it reciprocates in the cylinder 202. Reference numeral 203 represents a muffler, and has a muffler introduction port 204 defined therein for refrigerated gas extraction.

Reference numeral 205 represents a suction pad, and reference numeral 206 represents a suction reed having a reed valve 207. Reference numeral 208 represents a valve plate, which has two suction ports 210 defined therein and aligned with the reed valve 207. In addition, the valve plate 208 includes a first exhaust port 211, a first exhaust valve 212 to selectively open and close the first exhaust port 211, a second exhaust port 213, and a second exhaust valve 214 as The second exhaust port 213 and the through hole 214a are selectively opened and closed.

The first and second exhaust valves 212 and 214 are connected to each other by a valve end 214 b and are integrated, and the valve end 214 b is fixed to the valve plate 208 by a fixing member 215.

Reference numeral 216 represents an exhaust liner between the valve plate 208 and the cylinder head 217. By the sealing effect of the exhaust gasket 216, the exhaust chamber 218 facing the exhaust port 210 and the exhaust chamber 219 facing the exhaust ports 211 and 213 are formed in the cylinder head 217. The exhaust chamber 219 communicates with the exhaust muffler 221 via the through hole 214a.

The suction reed 206, the valve plate 208, and the cylinder head 217 are overlapped one by one and are mounted on the end surface of the cylinder 202 with bolts 200.

The operation and effects of the compressor valve mechanism structure described above will now be discussed.

As a result of the reciprocating movement of the piston 201, the refrigerated gas is guided from the muffler inlet 204 to the suction chamber 218 through the suction muffler 203 by the selective opening and closing effect of the reed valve 207, and then is sucked To the cylinder 202.

The refrigerant gas compressed in the cylinder 202 is discharged to the exhaust chamber after flowing through the first and second exhaust ports 211 and 213 by the selective opening and closing effects of the first and second exhaust valves 212 and 214 219, and then flows into the exhaust muffler 221 through the through hole 214a.

In Figure 7, because the first and second exhaust valves 212 and 214 are integrated with each other by connecting the valve end 214b, it has an effect that as long as the valve end 214b is fixed to the valve plate by the fixing member 215 208, it is possible to accurately and easily assemble the first and second exhaust valves 212 and 214 to the positions respectively aligned with the first and second exhaust ports 211 and 213, and therefore, the assembly can be performed fairly easily.

As illustrated in a cross-sectional view of the important part of the compressor valve mechanism shown in Figure 8, the first and second exhaust valves 211a and 213a can have different lengths D₁With D₂, Regarding the difference in length, they have different oscillation frequencies. The difference in the oscillation frequency makes the resonance generated by the exhaust valve different when the refrigerant is discharged. Therefore, the improvement effect of the exhaust efficiency can be appropriately adjusted to different revolutions. Among them, the improvement effect of the exhaust efficiency is when the resonance occurs. Will show up. At the same time, the increase of hiss caused by sound interference can be avoided, where the interference is generated when they have a very close resonance frequency, thus providing high efficiency and low noise properties.

It is worth noting that because an appropriate value related to the number of revolutions can be selected, it can bring the optimization effect at both high and low revolutions when performing a conversion drive.

In addition, because the appropriate value caused by the resonance of the exhaust valve changes in relation to the flow change caused by the load change, it has an optimal effect in both high load and low load.

As shown in Figure 9, the first and second exhaust valves 211b and 213b can have different widths W₁With W₂And, from the viewpoint of different widths, they can have different oscillation frequencies. The frequency of oscillation causes this resonance (generated by the exhaust valve when the refrigerant is discharged) to be different, and therefore, the effect of improving exhaust efficiency (which occurs when resonance occurs) can be appropriately adjusted to different number of revolutions. At the same time, the increase of hiss caused by the interference of sounds (when they have resonance frequencies close to each other) can be avoided, thus providing a high-efficiency and low-noise property.

It must be noted that, because an appropriate value can be selected in relation to the number of revolutions, when performing the conversion drive, both the high number of revolutions and the low number of revolutions can bring the optimization effect.

In addition, because the appropriate value caused by the resonance of the exhaust valve changes in relation to the flow change caused by the load change, it has an optimal effect in both high load and low load.

Figure 10 depicts an exploded view of an improved compressor valve mechanism of the present invention. The reference numeral 321 represents a first exhaust valve, and the reference numeral 322 represents a second exhaust valve, which is connected to the first exhaust valve 321 at a valve end 323 and is integrally formed. The first and second stoppers 324 and 325 are connected at the stopper end 326 and integrated with each other. By using a positioning pin 327 formed on the stopper end 326 to fix the valve end 323, the first exhaust valve 321 is adjusted up and down by the first stopper 324, while the second exhaust valve 322 is lifted by the second stopper 325. Adjust the lift. Therefore, as long as the stopper end 326 is fixed, it is possible to adjust the elevation of each of the first and second exhaust valves 321 and 322 very easily. At the same time, the first and second exhaust valves 321 and 322 can be assembled in positions aligned with the first and second exhaust ports 328 and 328, respectively, which brings about the effect that the assembly can be completed efficiently and easily.

The valve mechanism may be a structure shown in Figure 11. In Figure 11, reference numeral 331 represents a first exhaust valve, and reference numeral 332 represents a second exhaust valve, which is in contact with the first exhaust valve 331 The valve end 333 is connected and integrated. The first and second stoppers 334 and 335 are connected at the stopper end 336 and fixed by the valve end 333 to be integrated with each other. The first and second stoppers 334 and 335 have bending parts 337, the bending angles of which are respectively θ₁And θ₂, So the rising height at the respective ends 338 and 339 can be h₁With h₂。

Because the first and second exhaust valves 331 and 332 have different lifting heights, the movement of the refrigerated gas is different when the latter is discharged, and by providing a rising height commensurate with the number of revolutions or performance, the exhaust efficiency Can be optimized. In addition, it is possible to prevent an increase in fluid sound caused by interference (which occurs when the first and second exhaust valves 331 and 332 encounter similar active states).

The valve mechanism may be a structure as shown in Figure 12. In Figure 12, the reference numeral 341 represents the first exhaust valve, and the reference numeral 342 represents the second exhaust valve. The rising height has a different length L₁And L₂The first and second stoppers 346 and 347 are adjusted, and the lengths are measured from the bent portion 343 of the stopper end 342a to their free ends 344 and 345. From the point of view that the first and second stoppers 346 and 347 have different lengths, when the refrigerated gas is discharged, the individual positions where the first and second exhaust valves 341 and 342 contact their combined stoppers are different. Therefore, when the refrigerating gas is discharged, the individual activity states of the first and second exhaust valves 341 and 342 are different, and by providing an activity state commensurate with the number of revolutions or performance, the exhaust efficiency can be optimized change. In addition, it is possible to prevent an increase in fluid sound caused by interference (which occurs when the first and second exhaust valves 341 and 342 encounter similar active states).

Alternatively, the valve mechanism has a structure as shown in Fig. 13. In Fig. 13, reference numeral 351 represents a first exhaust valve, reference numeral 352 represents a second exhaust valve, and the reserved portion 353 of the first stopper 351a is connected to the second exhaust valve. The retaining parts 354 of the stopper 352a have different lengths A₁With A₂, And from this point of view, combine the effective valve parts 355 and 356 of the exhaust valve with the individual lengths S₁With S₂Are different from each other, so the exhaust valve has a different oscillation frequency. Different oscillation frequencies cause the resonance (generated by the exhaust valve when the refrigerant gas is discharged) to be different. Therefore, the improvement effect of the exhaust efficiency (shown when the resonance occurs) can be appropriately adjusted to different number of revolutions. At the same time, the increase of hiss caused by sound interference when their resonance frequencies are close to each other can be avoided, thus providing high efficiency and low noise quality.

It is worth noting that, because an appropriate value can be selected in relation to the number of revolutions, it can lead to an optimized effect at a high number of revolutions and a low number of revolutions when performing a conversion drive.

At the same time, because the appropriate value caused by the resonance of the exhaust valve changes in relation to the flow change caused by the load change, it has an optimal effect under high load and low load.

Figure 14 depicts an exploded view of another modified compressor valve mechanism of the present invention. The first and second exhaust ports 403 and 404 are defined in a groove 402 of the valve plate 401, and the first and second exhaust valves 405 and 405a are connected to the end of a valve and formed integrally with each other. Within the groove 402.

The first and second stoppers 407 and 408 are connected to a stopper end 409 and are integrally formed. A fixing portion 410 of the groove 402 is pressed against the valve end 406 to fix the valve end 406 in the groove. Within 402, the relative positions of the first exhaust valve 405 and the first exhaust port 403 are thus allowed to be determined, and the rising height of the first exhaust valve 405 is also allowed to be determined by the first stopper 407. Similarly, the relative position of the second exhaust valve 405 a and the second exhaust port 405 is determined, and the rising height of the second exhaust valve 405 a is determined by the second stopper 408. In addition, if the groove 402 has a depth equal to the sum of the stopper end 409 and the valve end 406, the stopper end 409 can be press-fitted and formed on the same plane of the valve plate 401, and the suction chamber 412 is the first The exhaust chamber 413 and the second exhaust chamber 414 can be formed in the cylinder head 411 by the valve plate 401, the stopper end 409 and the exhaust gasket 410.

In this way, by using the stopper end 409 to press-fit the valve end 406 into the groove 402, the exhaust port and the exhaust valve (one for each exhaust chamber) can be easily fitted in the two exhaust chambers. The ground is formed, highlighting excellent work ability. In addition, the hissing of the refrigerant caused by the selective opening and closing of the first exhaust valve 405 is generated in the first exhaust chamber 413, and at the same time, the hissing of the refrigerant caused by the selective opening and closing of the second exhaust valve 405a The sound is generated in the second exhaust chamber 414. Because the two will not interfere with each other, the abnormal sound caused by the interference of the refrigerant sound can be avoided.

According to the present invention, as described above, the installation of the exhaust valve of the compressor valve mechanism is easy, and a good working ability is obtained accordingly.

In addition, the compressor valve mechanism can exhibit a good exhaust efficiency and minimize the interference noise of the refrigerant gas, and therefore, minimize the noise emission.

In addition, the compressor valve mechanism can be obtained in which the first and second exhaust valves and the first and second stoppers can be easily fixed.

(Third embodiment)

Hereinafter, the third embodiment of the present invention will be described with reference to FIGS. 15 to 19.

Reference numeral 501 represents an electrically operated hermetic compressor, in which the compressor element 503 and the compressor unit 505 integrated with the electric motor 504 are elastically supported in the upper and lower regions of the hermetic box 502 by springs 506.

Reference numeral 507 represents a cylinder block in which a crankshaft 509 is supported by a bearing 508 and a piston 512 is connected to an eccentric part 510 by a connecting rod 511. Reference numeral 513 represents a valve plate provided with an exhaust port 514 and an exhaust port (not shown), and reference numeral 515 represents a reed valve to selectively open and close the exhaust port 514. Reference numeral 516 represents a cylinder head.

Reference numeral 517 represents an exhaust silencer, which is coupled to a passage 518 extending from the exhaust port 514 to the exhaust silencer 517. Reference numeral 519 represents a refrigerant flow branch pipe, which is provided so as to be open to enter a portion 519' of the passage 518. Reference numeral 520 denotes a refrigerant introduction port of the suction muffler 517. Reference numeral 521 represents a suction pipe extending through the sealed box 502 to be opposite to the refrigerant introduction port 520.

The operation of the electrically operated hermetic compressor with the structure described above will now be described.

When the reed valve 515 is opened during the pumping stroke of the compressor 501, the refrigerant gas enters the cylinder from the pumping muffler 517 through the passage 518. When the piston 512 is lifted into a compression stroke, the reed valve 515 is closed to rapidly interrupt the flow of the suction gas in the pipe 517, thereby increasing the internal pressure, allowing the air flow to flow into the refrigerant branch pipe 519 from the opening 519'.

In the subsequent pumping stroke, a negative pressure develops in the cylinder to allow the refrigerant gas to be immediately supplied from the refrigerant flow branch pipe 519, so that the refrigerant can be efficiently charged into the cylinder without releasing the flow inertia of the refrigerant.

In this way, the efficiency of the charge into the cylinder cannot be deteriorated, as happened in the early technology due to the intermittent flow of the pumped refrigerant gas, so the pumping efficiency can be maintained and improved.

As shown in FIG. 17, a refrigerant flow branch pipe 522 can be contained in the suction muffler 517, which can simplify the structure of the muffler 517 and improve the suction efficiency.

Alternatively, as shown in FIG. 18, the refrigerant flow branch pipes 523 and 524 of different lengths and the suction muffler 517 are integrated and connected to the passage 518.

In this case, when the number of revolutions of the electric-operated hermetic compressor is, for example, 50Hz and 60Hz, it is assumed that the shorter refrigerant flow branch pipe 523 and the longer refrigerant flow branch pipe 524 are tuned to 60Hz and 50Hz, respectively. The air columns in the refrigerant gas branch pipes 523 and 524 resonate at the respective number of revolutions. During the period when the reed valve 515 is closed, the refrigerant gas is filled into the refrigerant flow branch pipes 523 and 524, but during the period when the reed valve 515 is open, the function of the refrigerant flow pipes 523 and 524 is accelerated to the same as that of the refrigerant gas flowing into the cylinder. The loop is synchronous.

By doing this, with a simple muffler structure, an optimized air extraction efficiency can be improved at multiple revolutions.

It is worth noting that in the above description, the refrigerant flow branch pipes 523 and 524 are contained in the muffler 517. Even if they are constructed separately, similar effects can be obtained.

Alternatively, as shown in FIG. 19, the refrigerant flow branch pipe 525 may be housed in the suction muffler 517 and opened at 525' near the suction port 514.

By doing this, the flow inertia of the sucked refrigerant gas can be maintained and improved near the suction port 514, with a time delay (the refrigerant gas is discharged after passing through the refrigerant flow branch pipe 525 through the suction port 514 during the period when the reed valve 515 is opened. (Happens when entering the cylinder) can be minimized to further improve the pumping efficiency.

It is worth noting that as described above, the refrigerant flow branch pipes 525 are contained in the muffler 517. Even if they are constructed separately, similar effects can be obtained.

In FIGS. 15 to 19, the refrigerant introduction port 520 of the suction muffler 517 is formed to have a smaller cross-sectional area than the suction introduction port 514.

With the maintenance and improvement of the flow inertia of the refrigerant flow branch pipes 519, 522, 523, 524, and 525, the noise can be reduced by the cross-sectional throttling effect of the refrigerant gas inlet 520 (noise is emitted into an outlet of the sealed box 502) Effectively reduce the charging efficiency of the refrigerant into the cylinder without causing poorer charging efficiency.

As described above, according to the present invention, the intermittent flow phenomenon of refrigerant gas observed so far can be reduced and the flow inertia can be maintained and improved, resulting in an improvement in suction efficiency.

In addition, the structure can be simplified by integrating the suction muffler and the refrigerant flow branch pipe together.

In addition, by constructing a plurality of refrigerant flow branch pipes suitable for the respective number of revolutions, an optimal suction efficiency suitable for the specific number of revolutions can be obtained.

In addition, by opening the refrigerant flow branch pipe near the suction port, the suction efficiency can be further improved.

Also, by making the refrigerant gas introduction port of the suction muffler smaller than the suction port, noise can be reduced while maintaining the suction efficiency.

In this way, when compared with the earlier technology electric-operated hermetic compressors, the advantageous effects of high efficiency and low noise can be obtained.

(Fourth embodiment)

Hereinafter, the fourth embodiment of the present invention will be described with reference to FIGS. 15 and 20 to 23.

In FIG. 20, reference numeral 519 represents a refrigerant flow branch pipe, which is disposed on the passage 518 and has a tail end coupled with a sealed small chamber 530.

To describe the operation of the electrically operated hermetic compressor with the above structure, when the reed valve 515 is opened during the suction stroke of the compressor 501, the refrigerant gas enters the cylinder from the suction muffler 517 through the passage 518. When the piston 512 is lifted into a compression stroke, the reed valve 515 is closed to rapidly cut off the inhaled gas in the passage 518, accompanied by an increase in internal pressure (due to a flow inertia that fills the sealed chamber 530 through the branch pipe 519). Effect). Therefore, the upstream air flow in this passage is stopped. In the next inhalation stroke, the gas in the sealed chamber 530 immediately flows into the branch pipe 519. Therefore, the inhalation airflow becomes discontinuous and the initial airflow that occurred in the early technology is fully developed so that the delay time can be shortened, accompanied by an increase in the inhalation efficiency.

As shown in FIG. 21, a sealed small chamber 533 can be accommodated in the suction muffler 517. In addition to improving the suction efficiency, this structure also effectively simplifies the structure of the muffler.

Or, as shown in FIG. 22, the refrigerant flow branch pipes 534 and 535 of different lengths and the sealed small chambers 536 and 537 of different volumes are integrated with the suction muffler 517 and coupled with the passage 518. In this case, when the number of revolutions of the compressor is different, with a single muffler structure, an optimal suction efficiency can be increased in multiple revolutions. It is worth noting that the respective length and diameter of the branch pipes 534 and 535 and/or the respective volume of the sealed chamber may not always be limited to the above but each of them can be changed.

Or, as shown in FIG. 23, not only a sealed small chamber 538 is accommodated in the muffler 517, but also a refrigerant flow branch pipe 539 opens in the vicinity of the suction port 514. With this structure, any possible delay in air flow can be further reduced.

Accordingly, because the suction efficiency can be increased, the performance will not or rarely be degraded even if the cross section of the introduction port 520 of the suction getter 517 is reduced. Therefore, by the introduction port 520 which provides a throttling effect that allows the noise to be driven out into the cross-sectional area of the outlet of the sealed box 502, the noise can be reduced.

As described above, according to the embodiment of the present invention, the discontinuity of the refrigerant gas observed so far in the suction system of the early technology can be slowed down, and the suction efficiency can be increased, along with the improvement of the noise reduction performance in the muffler .

If the sealed chamber is placed in the suction muffler, the structure of the suction muffler can be simplified. In addition, if the sealed cell is configured to match the number of revolutions, the optimal efficiency can be increased among the number of revolutions. Furthermore, by arranging the outlet of the sealed cell near the suction port, the effect can be further increased. Also, with regard to performance, since the cross-sectional area of the inlet of the suction muffler can be reduced to a value smaller than the value of the suction port, the silencing performance can be sufficiently increased to provide a compressor with high performance.

Although the exemplified method of the present invention has been described quite completely with reference to the accompanying drawings, it is worth noting here that various changes and modifications are obvious to those skilled in the art. Therefore, unless these changes and modifications deviate from the spirit and scope of the present invention, they should be construed as being included therein.