HERMETIC COMPRESSOR

Abstract

In a stopper, by providing, in a position corresponding to a movable end vicinity of a discharge reed, a first regulation part having a predetermined clearance from the movable end vicinity of the discharge reed, since a hermetic compressor has such a two-stage spring characteristic that, until the movable end vicinity of the discharge reed touches the first regulation part, a spring characteristic is weak and, after the touch, the spring characteristic is strong, and there is obtained a discharge valve device which is easy to open and whose closing speed is rapid, it is possible to improve a delay in closing.

Description

TECHNICAL FIELD

The present invention relates to a discharge valve device of a hermetic compressor used mainly in a refrigeration/cold-storage apparatus and the like.

BACKGROUND ART

As a conventional hermetic compressor, there is, as disclosed in Japanese Patent Unexamined Publication No. 10-318146 for instance, one having possessed the discharge valve device in which there is contrived to reduce a noise at an operation time, and an energy efficiency is improved by reducing a loss at an opening/closing time of a discharge reed.

Hereunder, the above conventional hermetic compressor is explained while referring to the drawings. FIG. 13 is a sectional view of the conventional hermetic compressor, and FIG. 14 is a plan view of the conventional hermetic compressor. Further, FIG. 15 is an exploded view of the conventional hermetic compressor, FIG. 16 is a side sectional view of a discharge valve device of the conventional hermetic compressor, and FIG. 17 is a spring characteristic diagram of the conventional discharge valve device.

In FIG. 13, FIG. 14, FIG. 15, FIG. 16 and FIG. 17, hermetic container 401 possesses discharge pipe 402 and suction pipe 403, which are connected to a cooling system (not shown in the drawing). In a bottom part, oil 404 is stored, and motor element 407, which includes stator 405 and rotor 406, and compression mechanism 408 driven by it are accommodated, and an inside is filled with refrigerant 409.

Next, there is explained about a main constitution of compression mechanism 408. Cylinder 410 possesses substantially cylindrical compression chamber 411, and bearing part 412. Valve plate 413 possesses discharge valve device 414 in a side reverse to cylinder 410, and closes compression chamber 411. Head 415 covers valve plate 413.

Suction muffler 416 is constituted from tail pipe 417 that is a suction passage of a refrigerant gas, which has been opened into hermetic container 401, and a sound deadening space (not shown in the drawing), and the other end is communicated into compression chamber 411.

Crankshaft 418 has main shaft part 419 and eccentric part 420, and is shaft-supported to bearing part 412 of cylinder 410, and rotor 406 is pressing-in fixed. Piston 421 is inserted to cylinder 410 so as to be capable of reciprocating/sliding, and between it and eccentric part 420 is connected by connecting rod 422.

Next, there is explained about discharge valve device 414 possessed in compression mechanism 408. In valve plate 413, there are provided, in a side reverse to cylinder 410, discharge hole 423 communicating with cylinder 410, and valve seat part 424 having been formed so as to surround discharge hole 423. Discharge reed 425 consists of a leaf spring material, and possesses opening/closing part 426 for opening and closing valve seat part 424.

Head 415 possesses discharge chamber 427 accommodating discharge valve device 414, and monolithically forms stopper 428 regulating a degree of opening of discharge reed 425. Valve plate 413, discharge reed 425 and head 415 are disposed in this order, and monolithically connected to cylinder 410 side by bolt 429.

About the hermetic compressor having been constituted like the above, its operation is explained below. If electricity is supplied to motor element 407, rotor 406 rotates, and crankshaft 418 is rotation-driven. At this time, by the fact that an eccentric rotation motion of eccentric part 420 is transmitted to piston 421 through connecting rod 422, piston 421 performs a reciprocating motion in compression chamber 411.

Following upon the reciprocating motion of piston 421, refrigerant 409 in hermetic container 401 is sucked into compression chamber 411 from suction muffler 416, and refrigerant 409 of a low pressure flows into hermetic container 401 from the cooling system (not shown in the drawing) while passing through suction pipe 403. Refrigerant 409 having been sucked into compression chamber 411 is compressed by a motion of piston 421, and exhausted into discharge chamber 427 of head 415 via discharge valve device 414 of valve plate 413. Additionally, refrigerant 409 gas of a high pressure having been exhausted into discharge chamber 427 of head 415 is exhausted to the cooling system (not shown in the drawing) from discharge pipe 402.

At this time, the discharge valve device 414 performs such a predetermined opening/closing operation that, by the fact that discharge reed 425 opens, compression chamber 411 and discharge chamber 427 of head 415 are communicated through discharge hole 423 and, by the fact that discharge reed 425 closes, the communication between compression chamber 411 and discharge chamber 427 of head 415 is interrupted. However, in the above conventional constitution, discharge reed 425 can obtain only a constant spring characteristic until it touches stopper 428.

Here, about an operation of discharge valve device 414 is discussed in more detail. When discharge reed 425 of discharge valve device 414 opens, if a pressure difference between an inside of cylinder 410 and an inside of discharge chamber 427 of head 415 becomes large, opening/closing part 426 of discharge reed 425 is pushed up by compressed refrigerant 409 gas of the high pressure, it touches stopper 428.

Further, if the pressure difference between the inside of cylinder 410 and the inside of discharge chamber 427 of head 415 becomes small, opening/closing part 426 of discharge reed 425 separates from stopper 428 by a restoring force of an elastic deformation, thereby closing valve seat part 424.

That is, a spring characteristic of discharge reed 425, until it touches stopper 428, shows the constant spring characteristic having no inflection point as shown in FIG. 17. As a result, if the spring characteristic of discharge reed 425 is weakened, there is obtained the degree of opening of discharge reed 425 until it touches stopper 428, which has corresponded to a gas flow rate, by the constant spring characteristic, so that discharge reed 425 is easy to open, and it is possible to reduce an excessive compression. However, a speed when discharge reed 425 closes becomes slow and thus a delay in closing occurs, refrigerant 409 of the high pressure flows reversely in compression chamber 411, and a substantial displacement volume of piston 421 becomes small, so that a refrigerating ability lowers.

On the other hand, in a case where the spring characteristic of discharge reed 425 has been strengthened, reversely although discharge reed 425 is easy to close, it has a problem that a spring force when opening ascends and the excessive compression increases.

DISCLOSURE OF THE INVENTION

The hermetic compressor of the present invention is one in which the stopper is provided, in a position corresponding to a movable end vicinity of the discharge reed, with a first regulation part having a predetermined clearance from the movable end vicinity of the discharge reed, and can have such a two-stage spring characteristic that, until the movable end vicinity of the discharge reed touches the first regulation part, the spring characteristic is weak and, after the touch, the spring characteristic is strong.

By the constitution like this, since it is possible to have the two-stage spring characteristic, there is obtained the discharge valve device which is easy to open and whose closing speed is rapid, so that it is possible to provide a hermetic compressor in which the excessive compression is small, whose refrigerating ability is high, and in which the energy efficiency is high.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a sectional view of a hermetic compressor in an embodiment 1 of the present invention.

FIG. 2 is a plan view of the hermetic compressor in the embodiment 1 of the present invention.

FIG. 3 is an exploded view of a discharge valve device in the embodiment 1 of the present invention.

FIG. 4 is a side sectional view at a medium-term open time of the discharge valve device in the embodiment 1 of the present invention.

FIG. 5 is a side sectional view at a terminal open time of the discharge valve device in the embodiment 1 of the present invention.

FIG. 6 is a spring characteristic diagram of the discharge valve device in the embodiment 1 of the present invention.

FIG. 7 is a sectional view of a hermetic compressor in an embodiment 2 of the present invention.

FIG. 8 is a plan view of the hermetic compressor in the embodiment 2 of the present invention.

FIG. 9 is an exploded view of a discharge valve device in the embodiment 2 of the present invention.

FIG. 10 is a side sectional view at a medium-term open time of the discharge valve device in the embodiment 2 of the present invention.

FIG. 11 is a side sectional view at a terminal open time of the discharge valve device in the embodiment 2 of the present invention.

FIG. 12 is a spring characteristic diagram of the discharge valve device in the embodiment 2 of the present invention.

FIG. 13 is a sectional view of a conventional hermetic compressor.

FIG. 14 is a plan view of the conventional hermetic compressor.

FIG. 15 is an exploded view of a discharge valve device of the conventional hermetic compressor.

FIG. 16 is a side sectional view of the discharge valve device of the conventional hermetic compressor.

FIG. 17 is a spring characteristic diagram of the discharge valve device of the conventional hermetic compressor.

PREFERRED EMBODIMENTS FOR CARRYING OUT THE INVENTION

Hereunder, about embodiments of the present invention, there is explained by using the drawings.

Embodiment 1

FIG. 1 is a sectional view of a hermetic compressor in an embodiment 1 of the present invention, and FIG. 2 is a plan view of the hermetic compressor in the embodiment 1 of the present invention. Further, FIG. 3 is an exploded view of a discharge valve device in the embodiment 1 of the present invention, and FIG. 4 is a side sectional view at a medium-term open time of the discharge valve device in the embodiment 1 of the present invention. Further, FIG. 5 is a side sectional view at a terminal open time of the discharge valve device in the embodiment 1 of the present invention, and FIG. 6 is a spring characteristic diagram of the discharge valve device in the embodiment 1 of the present invention.

In FIG. 1, FIG. 2, FIG. 3, FIG. 4, FIG. 5 and FIG. 6, hermetic container 101 possesses discharge pipe 102 and suction pipe 103, which are connected to the cooling system (not shown in the drawing). In a bottom part, oil 104 is stored, and motor element 107, which includes stator 105 and rotor 106, and compression mechanism 108 driven by it are accommodated, and an inside is filled with refrigerant 109. Refrigerant 109 is desirably a refrigerant other than a specified flon object having corresponded to an environmental issue in recent years, and is R134a or R600a which is a natural refrigerant, or the like.

Next, there is explained about a main constitution of compression mechanism 108. Cylinder 110 possesses substantially cylindrical compression chamber 111, and bearing part 112. Valve plate 113 possesses discharge valve device 114 in a side reverse to cylinder 110, and closes compression chamber 111. Head 116 having formed discharge chamber 115 accommodating discharge valve device 114 covers valve plate 113. Suction muffler 117 is constituted from tail pipe 118 that is a suction passage of a refrigerant gas, which has been opened into hermetic container 101, and a sound deadening space (not shown in the drawing), and the other end is communicated into compression chamber 111.

Further, crankshaft 119 has main shaft part 120 and eccentric part 121, and is shaft-supported to bearing part 112 of cylinder 110, and rotor 106 is pressing-in fixed. Piston 122 is inserted to cylinder 110 so as to be capable of reciprocating/sliding, and between it and eccentric part 121 is connected by connecting rod 123.

Next, there is explained about discharge valve device 114 possessed in compression mechanism 108. In valve plate 113, there are provided, in a side reverse to cylinder 110, discharge hole 124 communicating with cylinder 110, and valve seat part 125 having been formed so as to surround discharge hole 124. Discharge reed 126 consists of a leaf spring material, and possesses opening/closing part 129 for opening/closing valve seat part 125.

Stopper 127 regulates the degree of opening of discharge reed 126 and possesses, in a position corresponding to a movable end vicinity of discharge reed 126, first regulation part 132 having provided a predetermined clearance from discharge reed 126. Further, stopper 127 possesses, in a position corresponding to opening/closing part 129 vicinity of discharge reed 126, second regulation part 133 having a clearance wider than first regulation part 132.

Discharge reed 126 and stopper 127 are disposed in this order, and monolithically connected and fixed to valve plate 113 by rivet 134.

About the hermetic compressor having been constituted like the above, its operation and action are explained below. If the electricity is supplied to motor element 107, rotor 106 rotates, and crankshaft 119 is rotation-driven. At this time, by the fact that the eccentric rotation motion of eccentric part 121 is transmitted to piston 122 through connecting rod 123, piston 122 performs the reciprocating motion in compression chamber 111.

Following upon the reciprocating motion of piston 122, refrigerant 109 in hermetic container 101 is sucked into compression chamber 111 from suction muffler 117, and refrigerant 109 of the low pressure flows into hermetic container 101 from the cooling system (not shown in the drawing) while passing through suction pipe 103. Refrigerant 109 having been sucked into compression chamber 111 is compressed, and exhausted into discharge chamber 115 via discharge valve device 114 of valve plate 113. Additionally, refrigerant 109 gas of the high pressure having been exhausted into discharge chamber 115 is exhausted to the cooling system (not shown in the drawing) from discharge pipe 102.

At this time, the discharge valve device 114 performs such an opening/closing operation that, by the fact that discharge reed 126 opens, compression chamber 111 inside and head 116 inside are communicated through discharge hole 124 and, by the fact that discharge reed 126 closes, the communication between compression chamber 111 and head 116 is interrupted.

Here, until discharge reed 126 touches first regulation part 132 of stopper 127, discharge reed 126 opens by a reaction force of refrigerant 109 gas of the high pressure. On this occasion, until discharge reed 126 touches first regulation part 132 of stopper 127, the constant spring characteristic having no inflection point is obtained and, by the fact that a first spring constant during this term is made small, the spring force is weakened, thereby making it easy to open.

Next, after discharge reed 126 has touched first regulation part 132 of stopper 127, since discharge reed 126 additionally bends with a site touching first regulation part 132 being made a supporting point, a second spring constant during this term becomes large in comparison with the first spring constant. As a result, after touching first regulation part 132, a strong reaction force of the spring is obtained by a strong spring force and, by the fact that this strong reaction force of the spring acts when discharge reed 126 has entered into its closing process, a speed at which discharge reed 126 closes becomes rapid.

Like the above, it is possible to have such a two-stage spring characteristic that, until the movable end vicinity of the discharge reed 126 touches first regulation part 132, the spring force is weak and, after the touch, the spring force is strong. Accordingly, there is obtained discharge valve device 114 which is easy to open and whose closing speed is rapid, so that it is possible to provide the hermetic compressor in which the excessive compression is small, whose refrigerating ability is high, and in which the energy efficiency is high.

In the embodiment 1, although there has been exemplified one in which one first regulation part 132 has been provided, by providing this plurally, it is possible to set a spring characteristic having possessed a more suitable easiness in opening and a more suitable reaction force in compliance with an opening of discharge reed 126 and, additionally, it is possible to provide the hermetic compressor in which the excessive compression is small, whose refrigerating ability is high, and in which the energy efficiency is high.

After discharge reed 126 has touched first regulation part 132 of stopper 127, if it opens additionally, it touches second regulation part 133. Since second regulation part 133 touches opening/closing part 129 vicinity of discharge reed 126, discharge reed 126 is scarcely displaced more than it. Accordingly, there is suppressed an increase in an internal stress occurring by a deformation of discharge reed 126, and, even under such a condition that a bending of discharge reed 126 becomes large by a liquid compression or the fact that the refrigerant gas having a high concentration, or the like is compressed, since it is possible to prevent an extreme increase in a stress of discharge reed 126, its breakage can be avoided, so that it is possible to obtain a high reliability.

Further, in a case where the liquid compression or the like has occurred, a large load is applied to opening/closing part 129 of discharge reed 126 by a liquid refrigerant whose density is high, and it is strongly pushed to a touching face of stopper 127. However, since stopper 127 is fixed to valve plate 113 by rivet 134, there is no fact that stopper 127 is removed, so that it is possible to provide the hermetic compressor whose reliability is high.

When discharge reed 126 touches the touching face of stopper 127, although discharge reed 126 undergoes an impact, in the embodiment 1, there is designed such that the touching face of stopper 127 is worked like an arc, and a stress of the impact applied to discharge reed 126 scarcely affects on a characteristic and a reliability of discharge valve device 114.

Embodiment 2

FIG. 7 is a sectional view of a hermetic compressor in an embodiment 2 of the present invention, and FIG. 8 is a plan view of the hermetic compressor in the embodiment 2 of the present invention. Further, FIG. 9 is an exploded view of a discharge valve device in the embodiment 2 of the present invention, and FIG. 10 is a side sectional view at a medium-term open time of the discharge valve device in the embodiment 2 of the present invention. Further, FIG. 11 is a side sectional view at a terminal open time of the discharge valve device in the embodiment 2 of the present invention, and FIG. 12 is a spring characteristic diagram of the discharge valve device in the embodiment 2 of the present invention.

In FIG. 7. FIG. 8, FIG. 9, FIG. 10, FIG. 11 and FIG. 12, hermetic container 201 possesses discharge pipe 202 and suction pipe 203, which are connected to the cooling system (not shown in the drawing). Hermetic container 201 stores, in its bottom part, oil 204 and accommodates motor element 207, which includes stator 205 and rotor 206, and compression mechanism 208 driven by it, and the inside is filled with refrigerant 209. Refrigerant 209 is desirably the refrigerant other than the specified flon object having corresponded to the environmental issue in recent years, and is R134a or R600a which is the natural refrigerant, or the like.

Next, there is explained about a main constitution of compression mechanism 208. Cylinder 210 possesses substantially cylindrical compression chamber 211, and bearing part 212. Valve plate 213 possesses discharge valve device 214 in a side reverse to cylinder 210, and closes compression chamber 211. Head 216 having formed discharge chamber 215 accommodating discharge valve device 214 covers valve plate 213. Suction muffler 217 is constituted from tail pipe 218 that is the suction passage of the refrigerant gas, which has been opened into hermetic container 201, and the sound deadening space (not shown in the drawing), and the other end is communicated into compression chamber 211.

Further, crankshaft 219 has main shaft part 220 and eccentric part 221, and is shaft-supported to bearing part 212 of cylinder 210, and rotor 206 is pressing-in fixed. Piston 222 is inserted to cylinder 210 so as to be capable of reciprocating/sliding, and between it and eccentric part 221 is connected by connecting rod 223.

Next, there is explained about discharge valve device 214 possessed in compression mechanism 208. In valve plate 213, there are provided, in a side reverse to cylinder 210, discharge hole 224 communicating with cylinder 210, and valve seat part 225 having been formed so as to surround discharge hole 224. Discharge reed 226 consists of the leaf spring material, and possesses opening/closing part 229 for opening and closing valve seat part 225.

Stopper 227 regulating the degree of opening of discharge reed 226 is formed monolithically with head 216, and has, in a position corresponding to a movable end vicinity of discharge reed 226, first regulation part 232 having a predetermined clearance from the movable end vicinity of discharge reed 226. Further, it has, in a position corresponding to opening/closing part 229, second regulation part 233 having a clearance larger than first regulation part 232.

Further, to touching faces of first regulation part 232 and second regulation part 233 there is fitted cap 234 having been molded from tetrafluoroethylene which is a solid lubricating material having a noncohesive property and having a refrigerant resistance, a chemical stability and a heat resistance. Valve plate 213, discharge reed 226 and head 216 are disposed in this order, and fixed to cylinder 210 side by bolt 235.

About the hermetic compressor having been constituted like the above, its operation and action are explained below. If the electricity is supplied to motor element 207, rotor 206 rotates, and crankshaft 219 is rotation-driven. At this time, by the fact that the eccentric rotation motion of eccentric part 221 is transmitted to piston 222 through connecting rod 223, piston 222 performs the reciprocating motion in compression chamber 211.

Following upon the reciprocating motion of piston 222, refrigerant 209 in hermetic container 201 is sucked into compression chamber 211 from suction muffler 217, and refrigerant 209 of the low pressure flows into hermetic container 201 from the cooling system (not shown in the drawing) while passing through suction pipe 203. Refrigerant 209 having been sucked into compression chamber 211 is compressed, and exhausted into head 216 via discharge valve device 214 of valve plate 213. Additionally, refrigerant 209 gas of the high pressure having been exhausted into discharge chamber 215 is exhausted to the cooling system (not shown in the drawing) from discharge pipe 202.

At this time, the discharge valve device 214 performs such an opening/closing operation that, by the fact that discharge reed 226 opens, compression chamber 211 inside and head 216 inside are communicated through discharge hole 224 and, by the fact that discharge reed 226 closes, the communication between compression chamber 211 and head 216 is interrupted.

Here, until discharge reed 226 touches first regulation part 232 of stopper 227, discharge reed 226 opens by the reaction force of refrigerant 209 gas of the high pressure. On this occasion, until discharge reed 226 touches first regulation part 232 of stopper 227, the constant spring characteristic having no inflection point is obtained and, by the fact that the first spring constant during this term is made small, the spring force is weakened, thereby making it easy to open.

Next, as shown in FIG. 10, after discharge reed 226 has touched first regulation part 232 of stopper 227, since discharge reed 226 additionally bends with a site touching first regulation part 232 being made the supporting point, the second spring constant during this term becomes large in comparison with the first spring constant. As a result, after touching first regulation part 232, the strong reaction force of the spring is obtained by the strong spring force and, by the fact that this strong reaction force of the spring acts when discharge reed 226 has entered into its closing process, the speed at which discharge reed 226 closes becomes rapid.

Like the above, since it is possible to have such a two-stage spring characteristic that, until the movable end vicinity of the discharge reed 226 touches first regulation part 232, the spring force is weak and, after the touch, the spring force is strong, there is obtained discharge valve device 214 which is easy to open and whose closing speed is rapid. Accordingly, it is possible to provide the hermetic compressor in which the excessive compression is small, whose refrigerating ability is high, and in which the energy efficiency is high.

In the embodiment 2, although there has been exemplified one in which one first regulation part 232 has been provided, by providing this plurally, it is possible to set the spring characteristic having possessed the more suitable easiness in opening and the more suitable reaction force in compliance with the opening of discharge reed 226 and, additionally, it is possible to provide the hermetic compressor in which the excessive compression is small, whose refrigerating ability is high, and in which the energy efficiency is high.

As shown in FIG. 11, after discharge reed 226 has touched first regulation part 232 of stopper 227, if it opens additionally, it touches second regulation part 233. Since second regulation part 233 touches opening/closing part 229 vicinity of discharge reed 226, discharge reed 226 is scarcely displaced more than it. Accordingly, there is suppressed the increase in the internal stress occurring by the deformation of discharge reed 226, and, even under such a condition that the bending of discharge reed 226 becomes large by the liquid compression or the fact that the refrigerant gas having the high concentration, or the like is compressed, it is possible to prevent the extreme increase in the stress of discharge reed 226, so that its breakage can be avoided and it is possible to obtain the high reliability.

In the embodiment 2, stopper 227 and head 216 are monolithically molded by a die casting and first regulation part 232 and second regulation part 233 are formed on the same die, so height dimensions of first regulation part 232 and second regulation part 233 reflect intact a die dimension accuracy. Normally, since the dimension accuracy of the die is controlled in several tens micron-meters or less, it is possible to obtain a high dimension accuracy without a necessity to especially work each face of first regulation part 232 and second regulation part 233, so that it is possible to cause a high production efficiency and a stable quality to coexist.

Further, in the embodiment 2, cap 234 is molded from a fluoric resin represented by the tetrafluoroethylene.

The tetrafluoroethylene is noncohesive, and possesses an extremely high solid lubricity. Accordingly, even if cap 234 and discharge reed 226 rub, since surfaces mutually slide while scarcely being caught, there is suppressed an abrasion by a metal contact occurring when discharge reed 226 touches stopper 227.

Additionally, the tetrafluoroethylene has a noncohesive nature, and thus discharge reed 226 is easy to be separated from stopper 227, so that it is possible to prevent a delay in closing of discharge reed 226 and increase the refrigerating ability of the hermetic compressor.

Since the tetrafluoroethylene is high in its vibration damping ability and has an elasticity, an impact when discharge reed 226 and stopper 227 touch is relaxed, a generation of an impact noise is suppressed, and further it is possible to prevent a breakage of discharge reed 226 by the impact, so that it is possible to provide a hermetic compressor which is silent and whose reliability is high.

An assembly is only to fit cap 234 having been previously molded by the fluoric resin to stopper 227, so that producibility is good as well.

In the embodiment 2, although the tetrafluoroethylene has been used as a solid lubricating material, even if there is used polybuthylene naphthalate, polybuthylene terephthalate or polyphenylene-sulfide is used as a resin material having possessed the similar nature, the similar action and effect are obtained.

INDUSTRIAL APPLICABILITY

Like the above, since the hermetic compressor concerned with the present invention can provide a hermetic compressor in which the delay in closing is improved and the energy efficiency has been raised, it can be applied also to uses of an air conditioner, a refrigeration/air-conditioning equipment, and the like.

REFERENCE MARKS IN THE DRAWINGS

110, 210 cylinder

113, 213 valve plate

114, 214 discharge valve device

115, 215 discharge chamber

116, 216 head

122, 222 piston

124, 224 discharge hole

125, 225 valve seat part

126, 226 discharge reed

127, 227 stopper

129, 229 opening/closing part

132, 232 first regulation part

133, 233 second regulation part

Claims

1. A hermetic compressor comprising:

a cylinder in which a piston performs a reciprocating motion;

a valve plate sealing an open end of the cylinder and having a discharge valve device in a side reverse to the cylinder; and

a head in which a discharge chamber for accommodating the discharge valve device is formed,

the discharge valve device including: a discharge hole communicating into the cylinder provided in the valve plate; a valve seat part formed in a side reverse to the cylinder at the discharge hole; a discharge reed formed of a leaf spring material and having an opening/closing part for opening and closing the discharge hole; and a stopper regulating an opening quantity of the discharge reed, and including a first regulation part having a predetermined clearance from the discharge reed at a position corresponding to a movable end vicinity of the discharge reed.

2. The hermetic compressor of claim 1, wherein the stopper includes a second regulation part having a clearance, which is wider than that of the first regulation part, at the position corresponding to the opening/closing part vicinity of the discharge reed.

3. The hermetic compressor of claim 1, wherein the discharge reed and the stopper are fixed to the valve plate.

4. The hermetic compressor of claim 1, wherein the stopper is molded in the head.

5. The hermetic compressor of claim 2, wherein touching faces of the first regulation part and the second regulation part are made of a solid lubricating material.