KR20060038911A - Hermetic compressor - Google Patents

Abstract

A hermetic compressor that has a pedestal of the valve plate to which a discharge reed equipped with an opening/closing part and discharge reed holding part, a spring reed equipped with a movable part and spring reed holding part, and a stopper equipped with a regulation part and stopper holding part, are fixed in this sequence, and also has a discharge valve device in which the spring reed is shaped in a substantially crank-like form is provided. A space is formed between the movable part of the spring reed and the opening/closing part of the discharge reed, and both are not adsorbed each other, thus preventing a delay in closing of the discharge reed. This makeup suppresses a decrease in freezing capacity of a fridge-freezer device and the like, thus implementing higher efficiency.

Description

Hermetic compressor {HERMETIC COMPRESSOR}

The present invention relates to hermetic compressors for use in refrigeration-freezers and the like.

Japanese Patent Laid-Open No. 2002-195160 discloses an example of a conventional hermetic compressor (hereinafter referred to as "compressor"). This is a compressor with a discharge valve device for reducing the noise during operation and the loss of opening and closing the discharge reed to improve energy efficiency.

Hereinafter, such a conventional compressor will be described with reference to FIGS. 7 to 10. Fig. 7 is a sectional view of a conventional compressor, Fig. 8 is a plan view of a conventional compressor, Fig. 9 is a side sectional view of a discharge valve device of a conventional compressor, and Fig. 10 is an exploded view of a discharge valve device of a conventional compressor.

The sealed container (hereinafter referred to as "container") 1 has a discharge pipe 2 and a suction pipe 3 both connected to a cooling system (not shown); Compression rotaryly driven by the electromechanical element 7, which consists of a stator 5 and a rotor 6 and stores oil 4 at its base; It houses a compression mechanism 8. The interior of the container 1 is filled with a refrigerant 9.

Next, the main structure of the compression mechanism 8 is demonstrated.

The cylinder 10 has a generally cylindrical compression chamber 11 and a bearing section 12. The valve plate 13 has a discharge valve device 14 on the opposite side of the contact surface to the cylinder 10 on the outside of the two sides of the valve plate 13 to close the compression chamber 11. Equipped. The head 15 covers the valve plate 13. A suction muffler 16 opens one end thereof into the container 1, and the other end of the suction muffler 16 communicates with the interior of the compression chamber 11. The crankshaft (17) has a main shaft (18) and an eccentric section (19), and the rotor (6) is press-fitted and held in a fixed state of the cylinder. It is pivotally supported by the bearing section 12. The piston 20 is inserted into the compression chamber 11 slidably in reciprocating motion and is connected to an eccentric section 19 with a connecting rod 21.

Next, the discharge valve apparatus 14 provided in the compression mechanism 8 is demonstrated.

The valve plate 13 has a recess 22 on the side opposite the cylinder 10. The recess 22 includes a discharge hole 23 communicating with the cylinder 10, a valve sheet 24 formed to surround the discharge port 23, a valve seat 24, It has a pedestal 25 formed generally on the same plane. The discharge lid 26, the spring lid 27 and the stopper 28 are in turn fixed to the pedestal 25 with rivets 29.

The discharge lid 26 made of a lingulate leaf-spring member includes a discharge reed holding part 30 fixed to the pedestal 25 and a valve seat 24. It is provided with an opening and closing portion 31 for opening and closing.

The spring lid 27 made of a tongue-shaped leaf spring member is provided with a spring lid fixing portion 32 fixed to a pedestal 25 and a movable part 33, and the opening and closing portion of the discharge lid 26 is provided. It has a bending part 34 near the base of 31.

The stopper 28 has a stopper fixing part 35 fixed to the pedestal 25 and a regulation part 36 for adjusting the operation of the discharge lead 26. The side of the adjuster 36 of the stopper 28 is formed generally parallel to the plane comprising the valve seat 24 and the pedestal 25. The movable portion 33 of the spring lid 27 is such that a predetermined clearance is formed between both the movable portion 33 and the opening and closing portion 31 of the discharge lead 26 and the adjusting portion 36 of the stopper 28. The angle of curvature of the curved portion 34 is adjusted.

Hereinafter, the operation of the compressor configured as described above will be described.

By supplying current to the electromechanical element 7, the rotor 6 is rotated and the crankshaft 17 is driven to rotate. In this case, as a result of the eccentric rotational movement of the eccentric section 19 being transmitted to the piston 20 via the connecting rod 21, the piston 20 reciprocates in the compression chamber 11.

When the piston 20 reciprocates, the coolant 9 in the container 1 is sucked from the suction muffler 16 into the compression chamber 11, and the low pressure coolant 9 is cooled through the suction pipe 3. It flows into the container 1 from a system (not shown). The coolant 9 sucked into the compression chamber 11 is compressed and discharged into the head 15 through the discharge valve device 14 of the valve plate 13. In addition, the high pressure gas discharged into the head 15 is discharged through a discharge pipe 2 to a cooling system (not shown).

However, in the above-described conventional configuration, the following phenomenon is sometimes observed. That is, the state of the low freezing capacity is maintained for a relatively long time compared to the original cooling capacity immediately after starting the compressor. This mechanism can be described as follows by analyzing the behavior of the discharge lead 26 and the spring lead 27.

When starting the compressor for which this phenomenon of low cooling capability is to be generated, the oil 4 is returned along the coolant 9 from a refrigeration cycle (not shown). A large amount of oil 4 intervenes in the discharge lid 26 and the spring lid 27 because the oil 4 as well as the coolant 9 is compressed and discharged.

In addition, the compressor is generally suctioned at high pressure when starting up, and compresses and discharges the coolant 9 of relatively high density until the inside of the container 1 is depressurized. Thus, a high load is applied to the opening and closing portion 31 of the discharge lead. On the other hand, the displacement of the opening / closing part 31 of the discharge lead 26 is adjusted by the adjusting part 36 of the stopper 28. As a result, the opening and closing portion 31 of the discharge lid 26 is movable part 33 of the spring lid 27 disposed between the opening and closing portion 31 and the adjusting portion 36 of the stopper 28 due to the high density coolant 9. Is strongly pressed against).

Thereafter, the high pressurization load as described above causes adsorption of the opening and closing portion 31 of the discharge lid 26 and the movable portion 33 of the spring lid 27 due to the oil 4. In this way, the discharge lead 26 and the spring lead 27 are integrated to perform the opening and closing operation as if it were one thick discharge lead.

Here, the movable part 33 of the spring lead 27 is bent in the curved part 34 in the direction in which the discharge lead 26 is opened, and as a result, the spring force is opposed to the direction in which the discharge lead 26 is closed. Act in the direction. In this way, the discharge lid 26 is pulled in the direction in which the discharge lid is opened, thereby delaying the closing time.

Therefore, after the piston 20 advances to the suction stroke in the compression chamber 11 through the top dead center, the time for the discharge lid 26 to open becomes long. On the other hand, the high pressure coolant flows back into the compression chamber 11, thereby reducing the significant volume displaced by the piston, resulting in a low cooling capacity phenomenon.

While this low cooling capacity phenomenon occurs, the compressor has reduced efficiency, increased power consumption, and at the same time, the cooling capacity of the cooler equipped with such a compressor is weakened.

Summary of the Invention

The present invention provides a hermetic compressor in which the side of the spring lead is formed in a generally crank-like shape, and the gap is formed between both the spring lead and the discharge lead and the stopper at a position corresponding to the discharge lead opening and closing portion.

This configuration prevents their adsorption and closing delay of the discharge leads caused by the oil interposed between the discharge leads and the spring leads, thus providing a highly efficient sealed compressor.

1 is a cross-sectional view of a compressor according to an embodiment of the present invention,

2 is a plan view of a compressor according to an embodiment of the present invention;

3 is a side cross-sectional view of a closed discharge valve device according to an embodiment of the present invention;

4 is an exploded view of a discharge valve device according to an embodiment of the present invention;

5 is a side cross-sectional view of an open discharge valve device according to an embodiment of the present invention;

6 is a diagram of the characteristics of the spring of the discharge valve device according to an embodiment of the present invention,

7 is a cross-sectional view of a conventional compressor,

8 is a plan view of a conventional compressor,

9 is a side sectional view of a discharge valve device of a conventional compressor;

10 is an exploded view of a discharge valve device of a conventional compressor.

The present invention relates to a compressor comprising a compression mechanism, a mechanism element for rotationally driving the compression mechanism, and a container for storing the oil and storing the compression mechanism and the mechanism element. The compression mechanism has a piston, a cylinder in which the piston reciprocates, and a valve plate that seals the open end of the cylinder and has a discharge valve device on opposite sides of the cylinder. The discharge valve device is formed on a valve plate having a discharge port communicating with the inside of the cylinder, a valve seat provided outside the discharge port, and a pedestal formed on the substantially same plane as the valve seat. In the discharge valve device, the discharge lead made of the leaf spring member includes an opening and closing portion for opening and closing the discharge port, and a discharge lead fixing portion fixed to the pedestal; The spring lead made of the leaf spring member has a movable portion and a spring lead fixing portion fixed to the pedestal; The stopper includes an adjusting portion and a stopper fixing portion fixed to the pedestal, and are fixed to the pedestal in this order. In addition, the side surface of the spring lead is generally formed in a crank shape, and a gap is formed between both the spring lead and the discharge lead and the stopper at a position corresponding to the discharge lead opening and closing portion. In this way, for example, at start-up, oil intervenes between the discharge lead and the spring lead, so that a space is formed between the movable part of the spring lead and the opening and closing part of the discharge lead even if an excessive load is applied on the discharge lead. This configuration prevents the delay of closing the discharge lead because both the moving part and the opening and closing part are not adsorbed to each other, thereby suppressing the decrease in the cooling capacity, thereby providing a compressor having high energy efficiency.

Further, in the compressor of the present invention, the bent portion of the discharge lead is bent toward the side of the valve seat at the side close to the opening and closing portion. In this way, since the force for pressing the opening and closing portion of the discharge lid against the valve seat is stably available, the sealability between the opening and closing portion of the discharge lid and the valve seat is improved, and the energy efficiency is also improved.

On the other hand, in the compressor of the present invention, the discharge lead bent portion is positioned at an undercut portion formed between the valve seat and the pedestal. Thereby, the inclination of the discharge lead can be stabilized, whereby the force for pressing the opening and closing portion of the discharge lead against the valve seat can be used stably. Thus, the sealing property between the opening and closing portion of the discharge lid and the valve seat is improved, and the energy efficiency is also improved.

Moreover, in the compressor of the present invention, a touch part is formed on the adjustment part of the stopper, which is curved toward the side of the spring lead. Thus, the method of supporting the spring lid's mobility is changed from the "cantilever" to the "center impeller" until the displacement of the discharge lid is adjusted by the stopper's adjuster, so that the spring lid's The spring force by the movable part can be utilized more efficiently in the meantime. This allows you to set the required spring characteristics step by step. Therefore, the optimum spring characteristic is available in both low and high circulation amounts, and also improves energy efficiency.

Hereinafter, an embodiment of a compressor according to the present invention will be described with reference to FIGS. 1 to 6. The figures here are schematic and do not accurately illustrate each positional relationship dimensionally.

Example

The container 101 has a discharge pipe 102 and a suction pipe 103 both connected to a cooling system (not shown); Oil 104 is stored at its base and contains a mechanism element 107 including a stator 105 and a rotor 106 and a compression mechanism 108 that is rotationally driven by the mechanism element 107. The interior of the container 101 is filled with the coolant 109.

Coolant 109 is preferably independent of chlorofluorocarbons (CFCs) corresponding to environmental problems in recent years, and coolants such as R134a and R600a are used.

Next, the main structure of the compression mechanism 108 is demonstrated.

The cylinder 110 has a generally cylindrical compression chamber 111 and a bearing section 112. The valve plate 113 has a discharge valve device 114 on the opposite side of the contact surface to the cylinder 110 on the outside of the two sides of the valve plate 113 to close the compression chamber 111. Head 115 covers valve plate 113. The suction muffler 116 opens one end thereof into the container 101, and the other end thereof communicates with the inside of the compression chamber 111. The crankshaft 117 has a main shaft 118 and an eccentric section 119, is pivotally supported by the bearing section 112 of the cylinder 110, and is press-fitted into the stator 105 to be fixed. The piston 120 is inserted into the compression chamber 111 so as to be slid in a reciprocating motion and connected to an eccentric section 119 with a connecting rod 121.

Next, the discharge valve device 114 provided in the compression mechanism 108 will be described. The valve plate 113 includes an outlet port 123 communicating with the cylinder 110, a valve seat 124 formed to surround the outlet port 123, and a pedestal 125 formed on a substantially same plane as the valve seat 124. Has a recess 122 with).

The discharge lead 126, the spring lead 127 and the stopper 128 are fixed to the pedestal 125 with rivets 129 in order. The discharge lead 126 made of a tongue-shaped leaf spring member includes a discharge lead fixing part 130 fixed to the pedestal 125 and an opening and closing part 131 for opening and closing the valve seat 124.

The spring lead 127 made of a tongue-shaped leaf spring member includes a spring lead fixing portion 132 fixed to the pedestal 125 and a movable portion 133, and includes a first curved portion provided on the movable portion 133. 134 and the second curved portion 135 is formed in a generally crank-like shape.

In addition, the first curved portion 134 is positioned near the base of the movable portion 133 of the spring lead 127, and the second curved portion 135 is positioned at the movable portion 133 of the spring lead 127.

The stopper 128 includes a stopper fixing part 136 fixed to the pedestal 125 and an adjusting part 137 for adjusting the operation of the discharge lead 126. The side of the adjuster 137 is formed generally parallel to the plane including the valve seat 124 and the pedestal 125.

The bending angle of each curved portion is set such that the movable portion 133 of the spring lid 127 has a gap between both the movable portion and the opening and closing portion 131 of the discharge lid 126 and the adjusting portion 137 of the stopper 128. .

The discharge lead curved portion 138 of the discharge lid 126 is curved toward the side of the valve seat 124 at the side close to the opening and closing portion 131.

An undercut portion 139 deeper than the pedestal 125 is formed between the valve seat 124 and the pedestal 125, and the discharge lead bend 138 is located within the undercut portion 139.

The stopper 128 forms a contact portion 140 that curves from the adjustment portion 137 of the stopper 128 to the side of the spring lid 127, and the side of the contact portion 140 has a valve seat 124 and a pedestal 125. It is formed generally parallel to the plane containing).

The operation and operation of the compressor configured as described above will be described.

By supplying current to the electromechanical element 107, the rotor 106 is rotated and the crankshaft 117 is driven rotationally. In this case, as a result of the eccentric rotational movement of the eccentric section 119 being transmitted to the piston 120 via the connecting rod 121, the piston 120 reciprocates in the compression chamber 111.

When the piston 120 reciprocates, the coolant 109 in the container 101 is sucked from the suction muffler 116 into the compression chamber 111, and the low pressure coolant 109 is cooled through the suction pipe 103. Flow into the container 101 from a system (not shown).

The coolant 109 sucked into the compression chamber 111 is compressed and discharged into the head 115 through the discharge valve device 114 of the valve plate 113. In addition, the high pressure gas discharged into the head 115 is discharged through a discharge pipe 102 to a cooling system (not shown).

Here, when starting the compressor, oil 104 is returned along with coolant 109 from a cooling cycle (not shown). A large amount of oil 104 intervenes between the drain reed 126 and the spring reed 127 because the oil 104 as well as the coolant 109 is compressed and discharged.

In addition, the compressor is generally suctioned at high pressure when starting up, and compresses and discharges a relatively high density of coolant 109 until the interior of the container 101 is depressurized. Therefore, a high load is applied to the opening and closing portion 131 of the discharge lead 126.

On the other hand, the displacement of the opening and closing portion 131 of the discharge lead 126 is adjusted by the adjusting unit 137 of the stopper 128. Accordingly, the opening and closing portion 131 of the discharge lid 126 is movable part 133 of the spring lid 127 disposed between the opening and closing portion 131 and the adjusting portion 137 of the stopper 128 due to the high density of the coolant 109. Strongly pressurized against.

This causes adsorption of the opening and closing portion 131 of the discharge lid 126 and the movable portion 133 of the spring lid 127 because of the oil 104.

However, since the first and second curved portions are formed in the movable portion 133 of the spring lead 127, as shown in FIG. 5, the opening portion 131 of the discharge lead 126 and the movable portion of the spring lead 127 are shown. A space 141 is formed between the 133. Thus, the movable portion 133 of the spring lid 127 is immediately separated from the opening and closing portion 131 of the discharge lid 126. In other words, adsorption does not last, and the spring lid 127 does not work in conjunction with the discharge lid 126, thereby preventing delay of closure.

Accordingly, the phenomenon of low cooling ability caused by the backflow of the high pressure coolant into the compression chamber 111 can be prevented, thereby providing a compressor having high energy efficiency.

On the other hand, the discharge lead curved portion 138 of the discharge lead 126 is curved toward the side of the valve seat 124 at the side close to the opening and closing portion 131, thereby opening and closing the opening and closing portion of the discharge lead 126 with respect to the valve seat 124. A force for pressing 131 is generated.

This force prevents the opening and closing portion 131 of the discharge lid 126 from floating above the valve seat 124 and maintains better sealing, thereby providing a compressor with high energy efficiency.

Furthermore, an undercut portion 139 formed deeper than the pedestal 125 is formed between the valve seat 124 and the pedestal 125, and the discharge lead bend 138 is located within the undercut portion 139, thus the undercut portion 139 ) Is prevented from being pressed by the spring force of the pedestal 125 and the spring lead 127. Accordingly, the inclination of the opening and closing portion 131 of the discharge lead 126 can be stabilized, whereby a compressor having a stable cooling capability is provided.

In addition, according to this embodiment, since the adjusting portion 137 of the stopper 128 is formed a contact portion 140 that is curved to the side of the spring lead 127, the discharge lead 126 is the spring lead 127 is the contact portion It may be displaced during contact with 140.

In other words, the spring characteristic of the discharge lead 126 has two inflection points, as shown in FIG. 6, so that three levels of spring force are available.

In Fig. 6, the horizontal axis shows displacement and the vertical axis shows spring force. "A" and "B" show the first and second bend points, respectively. Here, the first bending point is a point at which the opening and closing portion 131 of the discharge lead 126 contacts the movable portion 133 of the spring lead 127, and the force of the spring from the second bending point is determined by the discharge lead 126. The opening part 131 and the movable part 133 of the spring lead 127 can be used.

The second bend point is the point where the movable portion 133 of the spring lid 127 contacts the contact portion 140 of the stopper 128, and the spring supporting method is the spring as a result of the change from the "cantilever" to the "central impeller". Force increases.

As described above, the three stages of spring characteristics are achieved to have two bend points, and as the discharge lead 126 is greatly opened, a strong spring force is generated to allow the discharge lead 126 to close quickly.

In this way, the present invention provides a compressor having a high energy efficiency with a short delay in closing the discharge lid 126 even in a high circulation amount region in which the discharge lid 126 is largely opened.

The present invention provides a compressor with high energy efficiency with a very short delay in closing the discharge lead for a relatively large circulation amount. In addition, the compressor may use various types of coolant, and thus is applicable to cooling and air-conditioning devices using, for example, carbon dioxide (CO ₂ ) coolant.

Claims (4)

In hermetic compressors, With a compression mechanism, An electromotive element for rotationally driving the compression mechanism; A hermetic container for receiving the compression mechanism and the mechanism element and also storing oil; The compression mechanism, With the piston, A cylinder in which the piston reciprocates, A valve plate sealing the open end of the cylinder and having a discharge valve device on opposite sides of the cylinder, The discharge valve device, the discharge port in communication with the interior of the cylinder, A valve seat provided outside the outlet; It is formed with a pedestal which is formed in substantially the same plane as the valve seat, The pedestal, A discharge lead made of a leaf-spring member and having an opening and closing portion for opening and closing the discharge opening and a discharge lead fixing portion fixed to the pedestal; A spring lead made of a leaf spring member and having a movable lid and a spring lid fixing portion fixed to the pedestal; A stopper having an adjusting portion and a stopper fixing portion fixed to the pedestal, each of which is fixed to the pedestal in this order, One side of the spring lead is generally formed in a crank shape, and a clearance is formed between both the spring lead, the discharge lead, and the stopper at a position corresponding to the discharge lead opening and closing part. Hermetic compressor. The method of claim 1, Wherein the discharge lead is curved toward the side of the valve seat at the curved portion of the discharge lead proximate to the opening and closing portion. Hermetic compressor. The method of claim 2, The discharge lead bend is located in an undercut portion formed between the valve seat and the pedestal. Hermetic compressor. The method according to any one of claims 1 to 3, In the adjusting portion of the stopper, a contact part is formed that is bent and formed at a position close to the spring lead. Hermetic compressor.

Images