JP2009041481A - Enclosed compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an enclosed compressor which, while ensuring a discharge valve damping function, lowers the power consumption of the compressor by lowering the pressure within a cylinder at the start of discharge, and prevents an oil film-derived delay of a discharge valve upon the completion of discharge to increase a coolant circulation amount and thus to improve a compression capability. <P>SOLUTION: The enclosed compressor comprises: a valve plate 10 with a discharge hole 10a; a discharge valve plate 11 with a discharge valve part 11a, which is elastically deformed by gas pressure to close and open the discharge hole; and a damping plate 13 with a damping part 13a which, upon opening of the discharge valve part 11a, is allowed to abut thereagainst and, together with the discharge valve part 11a, is elastically deformed. The discharge valve plate 11 and the damping plate 13 are disposed so that a part as an elastically deformable fulcrum in the discharge valve part 11a is located at a position opposite an elastically deformable fulcrum in the damping part 13a, and that the front end side of the discharge valve part 11a is made abut against the front end side of the damping part 13a. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a hermetic compressor, and is particularly suitable for a hermetic compressor having a reciprocating piston used for a refrigerator, a room air conditioner, and the like.

  As a conventional hermetic compression machine, there is one disclosed in Japanese Patent Laid-Open No. 6-213159 (Patent Document 1).

  The hermetic compressor includes a piston, a cylinder in which the piston slides, a valve seat that seals the open end of the cylinder, a discharge valve device that is mounted on the opposite side of the valve seat, and the discharge valve device. And a cylinder head fixed to the valve seat via a gasket so as to cover. The discharge valve device includes a discharge valve fitted in a recess provided in a valve seat, and a backer valve that regulates the opening degree of the discharge valve.

  In the example shown in FIGS. 1 to 6 of Patent Document 1, a stepped gap is formed between the discharge valve and the backer valve, and the elastic force of the backer valve is discharged by the gap at the start of the compression process. Open the discharge valve smoothly without acting on the valve, and at the end of the compression process, the elastic force of the backer valve acts on the discharge valve to prevent delays in closing and reduce delays in opening and closing operations of the discharge valves It describes that the compression efficiency can be improved and the coefficient of performance can be increased.

  Moreover, in the example shown in FIGS. 7 to 9 of Patent Document 1, the backer valve is bent in the opening direction of the discharge valve at one bent portion on the fixed portion side. It is described that the same effects as those having a bent portion that forms a simple gap can be obtained.

JP-A-6-213159

  However, in Patent Document 1, since the fulcrum part (fixed part) of the discharge valve and the fulcrum part (fixed part) of the backer valve are located on the same side, the deformation direction of the discharge valve and the deformation direction of the backer valve are different. There is a risk that the oil film is formed between the two in contact with each other due to surface contact with the same inclination direction. In such a state, at the end of the compression process, the discharge valve is not easily detached from the backer valve due to the oil film force, causing a delay in closing the discharge valve and reducing the compression efficiency.

  Moreover, in patent document 1, since it was the structure which fits the discharge valve and backer valve which comprise a discharge valve apparatus in the recess provided in the valve seat, there existed a problem in the assembly property of the discharge valve apparatus.

  An object of the present invention is to reduce the power consumption of the compressor by reducing the pressure in the cylinder at the start of discharge while ensuring the function of damping the discharge valve, and to reduce the oil film of the discharge valve when the discharge is completed. It is an object of the present invention to provide a hermetic compressor capable of preventing the delay due to the increase in the refrigerant circulation amount and improving the compression capacity.

  Another object of the present invention is to reduce the power consumption of the compressor by reducing the pressure in the cylinder at the start of discharge while ensuring the function of damping the discharge valve, and to improve the assemblability. It is an object of the present invention to provide a hermetic compressor that can be used.

  The first aspect of the present invention for achieving the above-described object includes a cylinder having a cylinder chamber, a piston that reciprocates in the cylinder chamber, a discharge hole, and is fixed to the end face side of the cylinder. A valve plate, a discharge valve plate disposed on the opposite cylinder side of the valve plate, and having a discharge valve portion that elastically deforms by gas pressure received through the discharge hole to open and close the discharge hole; A hermetic compressor having a damping plate disposed on a cylinder block side and having a damping unit that elastically deforms together when the discharge valve plate is in contact when the discharge valve plate is opened. A portion serving as a fulcrum where the valve portion is elastically deformed and a portion serving as a fulcrum where the damping portion is elastically deformed are positioned on the opposite side, and the distal end side of the discharge valve portion is in contact with the distal end side of the damping portion So that the discharge valve plate In that it has installed fine the damper plate.

A more preferable specific configuration example in the first aspect of the present invention is as follows.
(1) A first spacer that forms a wall surface of a discharge space from the discharge hole between the discharge valve plate and the damping plate, and sets an interval between the damping portion and the discharge valve portion. Having provided.
(2) A stopper for restricting deformation of the damping unit is provided above the damping unit.
(3) A wall surface of the discharge space from the discharge hole is formed between the vibration control portion and the stopper, and a second spacer is provided for setting a distance between the vibration control portion and the stopper. .
(4) The first spacer is made thinner than the second spacer, and the interval between the damping unit and the discharge valve unit is made narrower than the interval between the damping unit and the stopper.
(5) forming the wall surface of the discharge space from the discharge hole and forming the discharge valve plate with a plate material having a discharge valve portion extending centrally from the wall surface, forming the wall surface of the discharge space from the discharge hole; The damping plate is composed of a plate material having a damping portion extending in the center from the wall surface, the wall surface of the discharge space from the discharge hole is formed, and the stopper is composed of a plate material having a stopper portion extending from the wall surface to the center. What you did.
(6) The discharge valve plate, the first spacer, the damping plate, the second spacer, and the stopper are provided with notches having different shapes so as to be visible.
(7) Notches of the discharge valve plate, the first spacer, the damping plate, the second spacer, and the stopper are formed in order from the valve plate side, and the outer peripheral portions are stacked in a stepped manner and can be visually observed. That.
(8) The colors of the first spacer and the second spacer are different from any of the discharge valve plate, the damping plate, and the stopper.

  Further, the second aspect of the present invention for achieving the above-mentioned another object includes a cylinder having a cylinder chamber, a piston that reciprocates in the cylinder chamber, a discharge hole, and an end face side of the cylinder. A valve plate that is fixed to the cylinder, a discharge valve plate that is disposed on the opposite cylinder side of the valve plate, and that has a discharge valve portion that opens and closes the discharge hole by being elastically deformed by gas pressure received through the discharge hole, A damping plate disposed on the side opposite to the cylinder block of the valve plate and having a damping portion that elastically deforms together when the discharge valve plate is in contact, and above the damping portion In a hermetic compressor provided with a stopper that is disposed and restricts deformation of the damping unit, a wall surface of a discharge space from the discharge hole is formed between the discharge valve plate and the damping plate. And the vibration control unit and the A first spacer for setting an interval with the valve outlet, and forming a wall surface of a discharge space from the discharge hole between the damping plate and the stopper; and the damping unit and the stopper A second spacer that sets a gap between the damping part and the discharge valve part to be larger than the gap between the damping part and the discharge valve part, forming a wall surface of the discharge space from the discharge hole and extending the discharge valve part from the wall surface to the center The discharge valve plate is constituted by a plate material having, a wall surface of a discharge space from the discharge hole is formed, and the vibration damping plate is constituted by a plate material having the vibration damping portion extending from the wall surface to the center, and from the discharge hole The stopper is constituted by a plate material that forms a wall surface of the discharge space and has a stopper portion extending in the center from the wall surface, the valve plate, the discharge valve plate, the first spacer, the damping plate, the second plate Spacers and The Tsu path lies in the fixed by common fasteners to be fixed to the cylinder.

A more preferable specific configuration example in the second aspect of the present invention is as follows.
(1) The discharge valve plate, the first spacer, the damping plate, the second spacer, and the stopper are configured in a shape or color that can be visually distinguished.

  According to the hermetic compressor of the first aspect of the present invention, it is possible to reduce the power consumption of the compressor by reducing the pressure in the cylinder at the start of discharge while securing the function of damping the discharge valve. Another object of the present invention is to provide a hermetic compressor capable of preventing the delay due to the oil film of the discharge valve at the completion of discharge and increasing the refrigerant circulation amount to improve the compression capacity.

  According to the hermetic compressor of the second aspect of the present invention, it is possible to reduce the power consumption of the compressor by reducing the pressure in the cylinder at the start of discharge while ensuring the function of damping the discharge valve. In addition, it is possible to improve the assemblability.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. The same reference numerals in the drawings of the respective embodiments indicate the same or equivalent.
(First embodiment)
A hermetic compressor according to a first embodiment of the present invention will be described with reference to FIGS.

  First, the whole hermetic compressor 50 of this embodiment will be described with reference to FIG. FIG. 1 is a longitudinal sectional view of a hermetic compressor 50 according to this embodiment.

  The hermetic compressor 50 according to the present embodiment is a reciprocating compressor in which the compression element 20 and the electric element 30 are arranged vertically in the hermetic container 3 and connected by the crankshaft 7. The compression element 20 and the electric element 30 are elastically supported by the sealed container 3.

  The compression element 20 includes a cylinder 1 that forms a cylinder chamber, a piston 4 that reciprocates in the cylinder chamber, a connecting rod 2 that drives the piston 4, and a number of components 9 to 17 that are assembled on the cylinder end face (see FIG. 2). ). The cylinder 1 is integrally formed with a bearing portion 1a and a frame 1b. The piston 4 is connected to the crankpin 7a via the connecting rod 2, and is reciprocated in the cylinder chamber by the eccentric rotation of the crankpin 7a.

  The electric element 20 is disposed below the frame 1 b and includes the stator 5 and the rotor 6. The stator 5 is fixed to the frame 1b, and the rotor 6 is fixed to the crankshaft 7. A crankpin 7a eccentric from the center of rotation is provided at the upper end of the crankshaft.

  The crankshaft 7 passes through the bearing portion 1a and extends upward from below the frame 1b, and is provided so that the crankpin 7a is positioned above the frame 1b. The lower part of the crankshaft 7 is directly connected to the rotor 6, and the crankshaft 7 is rotated by the power of the electric element 30. The crank pin 7 a and the piston 4 are connected by a connecting rod 2, and the piston 4 reciprocates via the crank pin 7 a and the connecting rod 2.

  The gas refrigerant supplied into the cylinder 1 is compressed by the reciprocating motion of the piston 4. The compressed gas refrigerant is sent to the discharge pipe via the discharge hole 10 a provided in the valve plate 10. The refrigerant sent to the discharge pipe is returned to the compressor again through the condenser, the decompression mechanism, and the evaporator. A refrigeration cycle is formed by a compressor, a condenser, a pressure reducing mechanism, and an evaporator. In this refrigeration cycle, a hydrocarbon-based refrigerant (HC refrigerant) such as propane (R290) or isobutane (R600a) is used.

  Refrigerating machine oil (lubricating oil) is stored in the hermetic container 17, and is pulled up by a pump action by the rotational movement of the crankshaft 7 and sent to the sliding portion of the compression element 20.

  Next, components assembled on the cylinder end face will be described with reference to FIGS. 2 is an exploded view of the parts 9 to 17 assembled on the cylinder end face of FIG. 1, FIG. 3 is a front view of the damping plate 13 of FIG. 2, and FIG. 4 is a view of the parts 11 to 13 assembled on the cylinder end face of FIG. FIG. 5 is a cut end view showing the periphery of the discharge hole 10a of the valve plate 10 of FIG.

  The parts assembled on the cylinder end face are, in order from the cylinder 1 side, the intake valve plate 9, the valve plate 10, the discharge valve plate 11, the thin plate spacer (first spacer) 12, the damping plate 13, the thick plate spacer (second plate). Spacer) 14, stopper 15, packing 16, and head cover 17.

  These components 9 to 17 are made of plate materials having substantially the same outer shape. Fastener through holes 18 are formed at the four corners of each component 9-17. Further, a suction hole 19 is formed in the central right part of each of the components 10 to 17. Furthermore, each component 11-17 has the outer peripheral part which forms the wall surface of the discharge space from the discharge hole 10a of the valve plate 10. As shown in FIG. The components 11 to 17 are installed such that their outer peripheral portions are stacked to form one discharge space.

And by passing fasteners, such as a volt | bolt, to the fastener through-hole 18 of these components 9-17, and fixing this fastener to the end surface of the cylinder 1, the components 9-17 are the end surface side of the cylinder 1 mentioned above. They are assembled and fixed in order. In other words, since the parts 9 to 17 are fixed to the end face side of the cylinder 1 with a common fastener, the assemblability can be improved. After the parts 9 to 17 are assembled, the parts 9 to 17 are controlled with the discharge valve plate 11. The gap dimension with the vibration plate 13 is defined by the thickness of the thin plate spacer 12, and the gap dimension between the vibration damping plate 13 and the stopper 15 is defined by the thickness of the thick plate spacer 14.

  Here, the thin plate spacer 12 is made thinner than the thick plate spacer 14. Thereby, the closing delay of the discharge valve plate 11 at the end of discharge can be further reduced. In addition, it is desirable that the thickness of the thin plate spacer 12 is 0.3 mm or less (most preferably 0.25 mm), and a space of 0.3 mm or less is secured between the discharge valve portion 11a and the vibration damping portion 13a.

  The valve plate 10 has a suction hole 19, a discharge hole 10 a and a discharge valve seat surface 10 b and is fixed to the end surface side of the cylinder 1.

  The discharge valve plate 11 has a discharge valve portion 11a that is disposed on the opposite cylinder side of the valve plate 10 and elastically deforms by gas pressure received through the discharge hole 10a to open and close the discharge hole 10a. Specifically, the discharge valve plate 11 is made of a flat plate material having a discharge valve portion 11a extending in the center from the wall surface of the outer peripheral portion forming the discharge space. The discharge valve portion 11a contacts the discharge valve seat surface 10b and closes the discharge hole 10a and the cylinder chamber.

  The damping plate 13 is disposed on the side opposite to the cylinder block of the discharge valve plate 11 and has a damping portion 13a that abuts the discharge valve portion 11a and elastically deforms together when the discharge valve portion 11a is opened. Yes. Specifically, the vibration damping plate 13 is made of a flat plate material having a vibration damping portion 13a extending in the center from the wall surface of the outer peripheral portion 13c forming the discharge space. Thus, the damping part 13a has a cantilever structure, and the tip side lower surface of the damping part 13a is in contact with the tip of the discharge valve part 11a. The damping portion 13a has a reduced contact area with the discharge valve portion 11a by the hole 13b, and reduces sticking due to surface tension that occurs when lubricating oil accumulates in the gap between the discharge valve portion 11a and the damping plate 13. ing.

  The discharge valve plate 11 and the damping plate 13 are located on the opposite side of a portion serving as a fulcrum where the discharge valve portion 11a is elastically deformed and a portion serving as a fulcrum where the damping plate 13a is elastically deformed, and the tip of the discharge valve portion 11a. It installs so that the space | interval of the side and the front end side of the damping part 13a may become the thickness of the thin-plate spacer 12. FIG.

  The stopper 15 has a stopper portion 15a that is disposed above the vibration damping portion 13a and restricts deformation of the vibration damping portion 13a. This stopper 15 is comprised with the flat board | plate material which has the stopper part 15a extended in the center from the wall surface of the outer peripheral part which forms discharge space.

  Next, with reference to FIGS. 5 to 7, the deformation operation of the discharge valve portion 11a and the vibration damping portion 13a and the change in the cylinder pressure when the compressed gas refrigerant passes through the discharge port 3a will be described. 6 is a cut end view highlighting the state of the discharge valve portion 11a and the damping portion 13a of FIG. 1 when deformed, and FIG. 7 shows the change in cylinder chamber pressure during discharge in the hermetic compressor of FIG. FIG.

  When the crankshaft 7 is driven, the piston 4 is driven via the crankpin 7a and the connecting rod 2. When the piston 4 approaches the valve plate side from the bottom dead center state, the cylinder chamber pressure rises beyond the discharge pressure as shown in FIG. In a state in which the discharge valve portion 11a is closed to the discharge valve seat surface 10b (see FIG. 3), the discharge valve portion 11a is not in contact with the vibration damping portion 13a, so that the front and rear are partitioned by the discharge valve portion 11a of the discharge valve plate 11 The force that opens the discharge valve portion 11a caused by the pressure difference in the space between the spring force of the discharge valve portion 11a and the surface tension generated by the lubricating oil between the discharge valve portion 11a and the discharge valve seat surface 10b If larger than this, the discharge valve portion 11a warps to the opposite valve plate side, and the discharge valve portion 11a opens from the discharge valve seat surface 10b (that is, the opening operation of the discharge valve portion 11a is started). Here, in a state where the discharge valve portion 11a is closed to the discharge valve seat surface 10b (see FIG. 5), the discharge valve portion 11a is not in contact with the vibration damping portion 13a, so at the moment when the discharge valve portion 11a opens, Regardless of the spring force of the damping part 13a, it is possible to prevent the opening delay of the discharge valve part 11a. As a result, the pressure in the cylinder at the start of discharge can be lowered to reduce the power consumption of the compressor.

When the opening operation of the discharge valve portion 11a is started, the compressed gas refrigerant in the cylinder chamber is discharged into the discharge space through the discharge hole 10a, so that the increase in the cylinder chamber pressure becomes moderate and the discharge valve portion 11a The tip side is brought into contact with the tip side of the vibration damping portion 13a. As a result, the damping function of the discharge valve portion 11 can be ensured. As the opening operation of the discharge valve portion 11a progresses, the pressure in the cylinder chamber eventually decreases, and the tip side of the discharge valve portion 11a and the damping portion. The tip end side of 13a is deformed as highlighted in FIG. That is, when the discharge valve portion 11a receives a force from the compressed gas refrigerant, the discharge valve portion 11a is deformed so as to warp opposite to the discharge valve seat surface 10b, and pushes up the damping plate 13. At this time, since the protruding direction of the damping plate 13 is opposite to the protruding direction of the discharge valve portion 11a, the discharge valve portion 11a and the damping portion 13a intersect with each other. The portion 11a and the vibration control portion 13a do not come into surface contact.

  Note that while the compressed gas refrigerant passes through the discharge hole 10a, the discharge valve portion 11a is deformed in the opening direction by the fluid force of the compressed gas refrigerant passing therethrough.

  As the discharge valve portion 11a advances to the fully open state and the cylinder chamber pressure decreases to near the discharge pressure, the fluid force of the compressed gas refrigerant decreases. Thereby, the discharge valve part 11a is returned to the valve plate side by the spring force of both the discharge valve part 11a and the damping part 13a, and the lift height of the discharge valve part 11a is lowered. As the lift height decreases, the flow path of the compressed gas refrigerant becomes narrower, and the cylinder chamber pressure rises again. As a result, the lift height of the discharge valve portion 11a increases, and the cylinder chamber pressure decreases again.

  Along with this, when the discharge valve part 11a is returned to the valve plate side by the spring force of both the discharge valve part 11a and the damping part 13a and the piston 4 comes to the top dead center, the flow of the compressed gas refrigerant stops. As a result, the force acting on the discharge valve portion 11a is lost, and the discharge valve portion 11a closes the discharge hole 10a to complete the discharge.

  Here, when the discharge plate 11 and the damping plate 13 are brought into surface contact with each other and an oil film is formed between them, and the adsorption phenomenon between the discharge plate 11 and the damping plate 13 due to the surface tension occurs, the piston 4 moves upward. It becomes a cause of time delay until the discharge valve portion 11a comes into contact with the seat surface 3b after reaching the dead point. Therefore, in the present embodiment, as described above, the protruding direction of the damping plate 13 is opposite to the protruding direction of the discharge valve portion 11a, and the direction in which the inclined direction of the discharging plate portion 11a intersects the inclined direction of the damping portion 13a. I have to. As a result, the discharge valve portion 11a and the damping portion 13a do not come into surface contact with each other, and the closing delay phenomenon of the discharge valve portion 11a can be prevented, so that the refrigerant circulation amount can be increased and the compression capacity can be improved.

  If the amount of warping of the discharge valve portion 11a is large when the piston 4 is at the top dead center position, the time until the discharge valve portion 11a closes the discharge hole 10a becomes longer, and the compressed gas refrigerant in the discharge pipe is discharged. It will flow back into the cylinder and reduce the efficiency of the compressor. Therefore, the gap between the discharge valve portion 11a and the damping portion 13a is made as small as possible so that the discharge valve portion 11a is as close as possible to the discharge hole 10a when the piston 4 is at a position near the top dead center.

However, when the discharge valve portion 11a starts the opening operation, if the discharge valve portion 11a and the damping portion 13a are in contact with each other, the force acting when the discharge valve portion 11a is opened is the discharge valve portion 11a. And the discharge valve seat surface 10b, the spring force of the discharge valve portion 11a, and the spring force of the damping portion 13a, the cylinder chamber pressure is equal to the spring force of the damping portion 13a. It is necessary to increase it, and the efficiency of the compressor decreases. Therefore, in the present embodiment, the thin plate spacer 12 is sandwiched between the discharge valve plate 11 and the damping plate 13, and a predetermined gap is formed between the discharge valve portion 11a and the damping portion 13a.
(Second Embodiment)
Next, a hermetic compressor according to a second embodiment of the present invention will be described with reference to FIGS. FIG. 8 is a diagram showing parts 10 to 15 assembled on the cylinder end face of the hermetic compressor according to the second embodiment of the present invention, and FIG. 9 is a part 10 on the cylinder end face of the hermetic compressor according to the second embodiment of the present invention. It is a figure which shows the state which assembled ~ 15. The second embodiment is different from the first embodiment in the points described below, and the other points are basically the same as those in the first embodiment, and thus redundant description is omitted.

  In this second embodiment, the discharge valve plate 11, the thin plate spacer 12, the damping plate 13, the thick plate spacer 14, and the stopper 15 are provided with notches 11c, 12c, 13c, 14c, and 15c having different shapes. Yes. The notches 11c, 12c, 13c, 14c, and 15c are provided in large order in order to form a step as shown in FIG. 9 after assembly.

Therefore, when the order of the discharge valve plate 11, the thin plate spacer 12, the damping plate 13, the thick plate spacer 14 and the stopper 15 is changed, the stairs are not uniform and the number of steps is reduced, so that the assembly state can be confirmed after assembly. The reliability of the hermetic compressor can be improved.
(Third embodiment)
Next, a hermetic compressor according to a third embodiment of the present invention will be described with reference to FIG. FIG. 10 is a view showing a state in which the parts 10 to 15 are assembled on the cylinder end surface of the hermetic compressor according to the third embodiment of the present invention. The third embodiment is different from the second embodiment in the following points, and the other points are basically the same as those in the second embodiment, and thus redundant description is omitted.

In the third embodiment, the discharge valve plate 11, the thin plate spacer 12, the damping plate 13, the thick plate spacer 14, and the stopper 15 have the same shape as the second embodiment, but the thin plate spacer 12 and the thick plate spacer 14 are made of brass. This is an example manufactured. Since brass is a color that is clearly different from other steel materials, the color of the staircase changes from step to step, making it easy to see the staircase. Therefore, when the order of the discharge valve plate 11, the thin plate spacer 12, the damping plate 13, the thick plate spacer 14, and the stopper 15 is changed, the stairs are uneven and the number of steps is reduced, so that the assembly state can be confirmed after assembly. The reliability of the hermetic compressor can be improved.
(Fourth embodiment)
Next, a hermetic compressor according to a fourth embodiment of the present invention will be described with reference to FIG. FIG. 11 is a view showing a state in which the parts 12 to 17 are assembled on the cylinder end surface of the hermetic compressor according to the fourth embodiment of the present invention. The fourth embodiment is different from the second embodiment in the following points, and the other points are basically the same as those in the second embodiment, and thus redundant description is omitted.

  In the fourth embodiment, the letter of the die-cut is added to the stepped portions corresponding to the notch portions 12c, 13c, 14c and 15c of the discharge valve plate 11, the thin plate spacer 12, the damping plate 13, the thick plate spacer 14 and the stopper 15. The characters appear when the parts are assembled in a normal state. Therefore, when there is an abnormality in the assembly state, the characters at the abnormal part cannot be visually recognized from the outside, so that the assembly operator can easily determine the abnormality.

  Also, a rivet hole (only the rivet hole 15d of the stopper 15 is shown) is provided, and the discharge valve plate 11, the thin plate spacer 12, the damping plate 13, the thick plate spacer 14 and the stopper 15 are assembled in advance and held by rivets. The workability when the head cover 8, the valve plate 10, and the suction valve plate 9 are attached to 1 is improved.

  With this structure, the assembly of the discharge valve plate 11, the thin plate spacer 12, the damping plate 13, the thick plate spacer 14, and the stopper 15 is improved, and furthermore, the structure can be easily discriminated after the assembly, so that it is sealed. The reliability of the compressor can be improved.

  With the hermetic compressor according to the fourth embodiment, when an actual machine test was performed at an operation speed of 1200 rpm to 4900 rpm, the volume efficiency did not decrease at a specific rotation speed, and all rotations The result which can maintain good efficiency in several ranges was obtained. In addition, it was possible to easily find abnormalities during assembly and to improve the reliability of the hermetic compressor.

  As described above, by adopting the structure of each embodiment including the fourth embodiment, the discharge valve portion 11a can be easily opened and the structure does not have a delay in closing, and the efficiency of the hermetic compressor is improved. Improvement and reliability improvement can be achieved.

It is a longitudinal cross-sectional view of the hermetic compressor of one embodiment of the present invention. It is an exploded view of the components assembled in the cylinder end surface of FIG. It is a front view of the damping board of FIG. It is a front view of the components assembled in the cylinder end surface of FIG. FIG. 2 is a cut end view showing the periphery of a discharge hole of the valve plate of FIG. 1. FIG. 2 is a cut end view that emphasizes and shows the state of the discharge valve portion and the vibration damping portion of FIG. 1 during deformation. It is a figure which shows the change of the cylinder chamber pressure at the time of discharge in the hermetic compressor of FIG. It is a figure which arranges and shows the parts assembled in the cylinder end face of the hermetic compressor of a 2nd embodiment of the present invention. It is a figure which shows the state which assembled the components to the cylinder end surface of the hermetic compressor of 2nd Embodiment of this invention. It is a figure of the state which assembled the components to the cylinder end surface of the hermetic compressor of a 3rd embodiment of the present invention. It is a figure of the state which assembled the components to the cylinder end surface of the hermetic compressor of a 4th embodiment of the present invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Cylinder, 2 ... Connecting rod, 3 ... Sealed container, 4 ... Piston, 5 ... Stator, 6 ... Rotor, 7 ... Crankshaft, 7a ... Crankpin, 9 ... Suction valve plate, 10 ... Valve plate, 10a ... Discharge Holes, 10b ... discharge valve seat surface, 11 ... discharge valve plate, 11a ... discharge valve part, 12 ... thin plate spacer (first spacer), 13 ... damping plate, 13a ... damping part, 13b ... hole part, 14 ... thick plate spacer (second spacer), 15 ... stopper, 15a ... stopper portion, 16 ... packing, 17 ... head cover, 18 ... fastener through hole, 19 ... suction hole, 20 ... compression element, 30 ... electric element, 50: Hermetic compressor.

Claims (11)

A cylinder forming a cylinder chamber;
A piston that reciprocates in the cylinder chamber;
A valve plate having a discharge hole and fixed to the end face side of the cylinder;
A discharge valve plate that is disposed on the opposite cylinder side of the valve plate and has a discharge valve portion that elastically deforms due to gas pressure received through the discharge hole and opens and closes the discharge hole;
A vibration-damping plate that is disposed on the side opposite to the cylinder block of the discharge valve plate and has a vibration-damping portion that elastically deforms together when the discharge valve plate is in contact with the discharge valve plate. In the compressor,
The portion serving as a fulcrum for elastically deforming the discharge valve portion and the portion serving as a fulcrum for elastically deforming the vibration damping portion are positioned on the opposite side, and the distal end side of the discharge valve portion is in contact with the distal end side of the vibration damping portion As described above, the hermetic compressor is provided with the discharge valve plate and the damping plate.   In Claim 1, the wall surface of the discharge space from the said discharge hole is formed between the said discharge valve plate and the said damping plate, and the 1st which sets the space | interval of the said damping part and the said discharge valve part A hermetic compressor provided with a spacer.   The hermetic compressor according to claim 2, further comprising a stopper that restricts deformation of the damping unit above the damping unit.   The second spacer according to claim 3, wherein a wall surface of a discharge space from the discharge hole is formed between the damping unit and the stopper, and a second spacer is provided for setting a distance between the damping unit and the stopper. A hermetic compressor characterized by that.   In Claim 4, The said 1st spacer was made thinner than the 2nd spacer, and the space | interval of the said damping part and the said discharge valve part was narrowed rather than the space | interval of the said damping part and the said stopper. A hermetic compressor.   5. The discharge valve plate according to claim 4, wherein the discharge valve plate is formed of a plate material that forms a wall surface of the discharge space from the discharge hole and has a discharge valve portion extending from the wall surface to the center, and forms a wall surface of the discharge space from the discharge hole. And the damping plate is constituted by a plate material having a damping portion extending in the center from the wall surface, the wall surface of the discharge space from the discharge hole is formed, and the stopper is formed by a plate material having a stopper portion extending from the wall surface to the center. A hermetic compressor characterized by comprising   In Claim 6, the notch from which a shape differs in each outer peripheral part of the said discharge valve plate, the said 1st spacer, the said damping plate, the said 2nd spacer, and the said stopper was provided visually. Hermetic compressor.   8. The discharge valve plate, the first spacer, the damping plate, the second spacer, and the stopper notches are formed in order from the valve plate side, and the outer peripheral portions are stacked stepwise. A hermetic compressor characterized by being visible.   6. The hermetic compressor according to claim 5, wherein the first spacer and the second spacer are colored different from any of the discharge valve plate, the damping plate, and the stopper. A cylinder forming a cylinder chamber;
A piston that reciprocates in the cylinder chamber;
A valve plate having a discharge hole and fixed to the end face side of the cylinder;
A discharge valve plate that is disposed on the opposite cylinder side of the valve plate and has a discharge valve portion that elastically deforms due to gas pressure received through the discharge hole and opens and closes the discharge hole;
A damping plate that is disposed on the side opposite to the cylinder block of the discharge valve plate, and has a damping portion that elastically deforms together when the discharge valve plate is in contact, and
In a hermetic compressor provided with a stopper that is disposed above the vibration suppression unit and restricts deformation of the vibration suppression unit,
A first spacer is provided between the discharge valve plate and the damping plate to form a wall surface of the discharge space from the discharge hole and set a distance between the damping portion and the discharge valve portion,
A wall surface of the discharge space from the discharge hole is formed between the damping plate and the stopper, and an interval between the damping portion and the stopper is determined by an interval between the damping portion and the discharge valve portion. A second spacer that is set larger,
The discharge valve plate is formed of a plate material that forms the wall surface of the discharge space from the discharge hole and has the discharge valve portion extending in the center from the wall surface, and forms the wall surface of the discharge space from the discharge hole. The damping plate is constituted by a plate material having the damping part extending from the center to the center, the wall of the discharge space from the discharge hole is formed, and the stopper is constituted by a plate having a stopper part extending from the wall to the center. ,
A hermetic compressor characterized in that the valve plate, the discharge valve plate, the first spacer, the damping plate, the second spacer, and the stopper are fixed by a common fastener for fixing the cylinder. .   11. The hermetic compressor according to claim 10, wherein the discharge valve plate, the first spacer, the damping plate, the second spacer, and the stopper are configured in a shape or color that can be visually distinguished. .

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