JP2008002370A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor improving reliability of valve devices and having high efficiency. <P>SOLUTION: At least one of the valve devices 160 comprises a communication hole 156, a valve seat surface formed on an outer periphery of the communication hole 156, and a cantilevered reed valve 157 for opening and closing the valve seat surface. An area of the valve seat surface on a distal end side of the reed valve 157 is set to be larger than an area of the valve seat surface on a counter-distal end side of the reed valve. A portion where impact load from a lead is large is formed in the large area and therefore the impact load caused by collision of the reed valve and the valve seat surface is reduced. The area of the valve seat surface on a lead holding side where impact load from the lead is small is made small so that adhesion of the reed valve and the valve seat surface can be reduced, delay in opening of the reed valve can be prevented and both high efficiency and reliability can be attained. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a compressor used for a refrigerator, an air conditioner and the like.

  Conventionally, there is a compressor of this type provided with a valve device for discharge and suction (see, for example, Patent Document 1).

  The conventional compressor will be described below with reference to the drawings.

  11 is a cross-sectional view showing a conventional compressor described in Patent Document 1, and FIG. 12 is an exploded perspective view showing a conventional valve device.

  11 and 12, oil 10 is sealed in a sealed container 41, and a compression mechanism 1 that sucks and compresses refrigerant and an electric element 5 that drives the piston 3 are housed.

  The compression mechanism 1 is configured by attaching a valve plate 11 having a suction hole 7 and a discharge hole 9 to an end of a cylinder 13 and further attaching a cylinder head 15.

  A discharge hole 9 is formed in the valve plate 11, and a discharge valve seat surface 23 formed of a ring-shaped flat surface is formed concentrically with the discharge hole 9.

  The valve plate 11 is formed with a suction hole 7 and a suction valve seat surface 25 formed of a ring-shaped flat surface concentrically with the suction hole 7.

  The discharge reed valve 19 is elastically deformed with one side as a fulcrum, and the discharge hole 9 is opened and closed intermittently by opening and closing the discharge valve seat surface 23.

  The suction reed valve 17 is elastically deformed with one side as a fulcrum, and the suction hole 7 is opened and closed intermittently by opening and closing the suction valve seat surface 25.

  The retainer 21 is formed to regulate the lift amount when the discharge reed valve 19 is opened and closed.

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

  Electric power supplied from a commercial power source (not shown) is supplied to the electric element 5 and rotates the rotor 27 of the electric element 5.

  The rotor 27 rotates the crankshaft 29, and the eccentric movement of the eccentric portion 31 drives the piston 3 from the connecting rod 33 of the connecting means via the piston pin 35, whereby the piston 3 reciprocates in the bore 37.

  The refrigerant introduced into the sealed container 41 through the suction tube 39 is continuously compressed in the bore 37 from the suction muffler 43 through the suction hole 7 and discharged from the discharge hole 9 to the cylinder head 15.

At this time, the discharge reed valve 19 is elastically deformed with one side serving as a fulcrum and intermittently collides with the discharge hole 9 by opening and closing the discharge valve seat surface 23, and the suction reed valve 17 is elastically deformed with one side serving as a fulcrum and the intake valve Opening and closing the seat surface 25 intermittently collides with the suction hole 7, but is interposed between the discharge reed valve 19 and the discharge valve seat surface 23 and between the suction reed valve 17 and the suction valve seat surface 25. Oil 10 acts as a damper to alleviate this impact.
JP 2001-32773 A

  However, in the configuration of the conventional valve device described above, when the oil viscosity decreases at a high temperature and the oil holding power decreases, there is a possibility that the oil runs out and the damper effect cannot be sufficiently obtained. As a result, the impact load applied to the lead is increased and the lead may be damaged.

  On the other hand, if the valve seat surface is widened to reduce the impact load on the reed to stabilize the oil retention, the viscous resistance due to oil on the reed and the seat increases at normal temperatures, and the reed opening timing is delayed. , Had the problem of a significant drop in efficiency.

  The present invention solves the above-described conventional problems, and an object thereof is to provide a compressor that achieves both high efficiency and high reliability.

  In order to solve the above-mentioned conventional problems, the compressor of the present invention has an area of the valve seat surface on the tip side of the reed valve that is larger than the area of the valve seat surface on the opposite end side of the reed valve. The impact load due to the collision between the reed valve and the valve seat surface is reduced on the valve seat surface on the tip side of the large reed valve, and the impact load of the reed is small. The adhesive force between the reed valve and the valve seat surface can be kept small, and the reed valve can be prevented from delaying the opening.

  The compressor of the present invention can provide a compressor that achieves both high efficiency and reliability by increasing the area of the valve seat surface on the leading end side of the lead and decreasing the area of the valve seat surface on the lead restraining section side. it can.

  According to the first aspect of the present invention, oil is stored in a sealed container and a compression mechanism is accommodated, and the compression mechanism includes a valve device that opens and closes in a suction and compression stroke, and at least one of the valve devices includes a communication hole. And a valve seat surface formed on the outer periphery of the communication hole, a cantilevered reed valve that opens and closes the valve seat surface, and an area of the valve seat surface on the tip side of the reed valve is set to be opposite to the reed valve. It is larger than the area of the valve seat surface on the tip side, and the part where the impact load of the reed is large is configured with a wide area, so the impact load due to the collision between the reed valve and the valve seat surface is reduced, and the lead By reducing the valve seat area on the side of the reed holding part where the impact load is small, the adhesive force between the reed valve and the valve seat surface can be kept small, and delay in opening the reed valve can be prevented. And reliability Door can be.

  The invention according to claim 2 is such that both the outer peripheral shape and the inner peripheral shape of the valve seat surface are circular, and in addition to the invention according to claim 1, the processability is further improved in manufacturing the valve device. Good productivity can be improved.

  The invention according to claim 3 is the one in which the chamfering is performed on the inner peripheral side of the valve seat surface, and the contact between the reed valve and the valve seat surface is changed from line contact to surface contact, and the impact load is reduced. In addition to the effect of the invention described in claim 1 or 2, it is possible to operate without further reducing the reliability.

  Invention of Claim 4 uses the hydrocarbon refrigerant | coolant which does not contain chlorine and a fluorine as a refrigerant | coolant, and uses the oil compatible with the said refrigerant | coolant. In addition to the effects of the described invention, even if the refrigerant is dissolved in the oil and the oil viscosity is lowered, the operation can be performed without reducing the reliability.

  According to a fifth aspect of the present invention, the compression element is driven at an operating frequency that includes at least a rotational speed higher than the power supply frequency. In addition to the effects of the first aspect of the present invention, Furthermore, even at high speed rotation where the impact load of the lead becomes large, the operation can be performed without reducing the reliability.

(Embodiment 1)
1 is a cross-sectional view of a compressor according to a first embodiment of the present invention, FIG. 2 is a longitudinal cross-sectional view of a suction valve device according to the first embodiment, and FIG. 3 is a main part of the suction valve device according to the first embodiment. FIG. 4 is a detailed view, FIG. 4 is a plan view of the suction valve device in the same embodiment, and FIG. 5 is a plan view of the suction reed valve of the suction valve device in the same embodiment.

  1 to 5, the sealed container 101 accommodates a stator 103, an electric element 105 including a rotor 104, and a compression mechanism 106 driven by the electric element 105. The refrigerant sealed in the sealed container 101 is a hydrocarbon refrigerant that does not contain chlorine and fluorine.

  An oil 108 that is compatible with the refrigerant is stored in the sealed container 101. The oil 108 is a mineral oil compatible with a hydrocarbon refrigerant, and has a viscosity of 5 to 10 centistokes.

  The suction tube 150 is fixed to the sealed container 101 and connected to the primary side (not shown) of the apparatus, and guides a fluid (not shown) into the sealed container 101.

  Next, details of the compression mechanism 106 will be described below.

  The electric element 105 includes a stator 103 and a rotor 104, and is configured by an inverter-driven motor that is driven at a plurality of arbitrary operation frequencies including a rotational speed higher than at least a power supply frequency such as 70 Hz.

  The crankshaft 110 includes a main shaft portion 112 in which the rotor 104 is press-fitted and fixed, and an eccentric portion 113 formed eccentric to the main shaft portion 112.

  A stator 103 is fixed to the cylinder block 115, a substantially cylindrical bore 122 is formed, and a bearing portion 133 that supports the main shaft portion 112 is provided.

  The piston 135 loosely fitted in the bore 122 is connected to the eccentric portion 113 via a piston pin 136 by a connecting rod 140 that is a connecting means. The end surface of the bore 122 is sealed with a valve plate 145.

  The head 146 forms a high-pressure chamber and is fixed to the side opposite to the bore 122 of the valve plate 145.

  The suction muffler 152 is sandwiched between the valve plate 145 and the head 146.

  A discharge valve device (not shown) is formed on the valve plate 145 on the head 146 side. A communication hole 156 is formed in the valve plate 145, and a suction valve seat surface 155 is formed around the communication hole 156 on the bore 122 side, and constitutes a suction valve device 160 together with the suction reed valve 157.

  The valve plate 145 is formed of a sintered metal material, and the suction valve seat surface 155 is formed of a sintered mold.

  The suction reed valve 157 is made of a leaf spring material, and opens and closes the suction valve seat surface 155 by elastically deforming one side with the fulcrum portion as a fulcrum.

  The suction valve seat surface 155 is circular in both outer peripheral shape and inner peripheral shape, and the centers thereof are offset from each other in the longitudinal direction of the suction reed valve 157. As a result, the area of the front valve seat surface 157a corresponding to the front end side of the suction reed valve 157 is larger than the area of the anti front end valve seat surface 157b corresponding to the opposite side of the suction reed valve 157.

  In addition, the outer peripheral side and inner peripheral side end portions of the suction valve seat surface 155 are each provided with an R chamfer 163 over the entire circumference.

  About the compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  Electric power supplied from a commercial power source (not shown) is supplied to the electric element 105 to rotate the rotor 104 of the electric element 105.

  The rotor 104 rotates the crankshaft 110, and the eccentric movement of the eccentric portion 113 drives the piston 135 from the connecting rod 140 of the connecting means via the piston pin 136, whereby the piston 135 reciprocates in the bore 122, and the suction tube The fluid introduced into the sealed container 101 through 150 is sucked from the suction muffler 152 through the suction valve device 160 and continuously compressed in the bore 122.

  During the continuous compression, the suction reed valve 157 continuously collides with the suction valve seat surface 155 during the opening / closing operation.

  At this time, the tip side of the suction reed valve 157 has a higher opening / closing speed, so the collision speed with the suction valve seat surface 155 is higher.

  However, in the present embodiment, the area of the front valve seat surface 157a corresponding to the front end side of the suction reed valve 157 is larger than the area of the anti front end valve seat surface 157b corresponding to the opposite side of the suction reed valve 157. Therefore, since the tip end side of the suction reed valve 157 is received in a wide area, the impact load generated when the suction reed valve 157 collides with the tip side valve seat surface 157a is reduced and reduced.

  As a result, damage to the suction reed valve 157 can be prevented.

  On the other hand, the area of the anti-leading valve seat surface 157b of the suction reed valve 157 having a small impact load is made smaller than that of the leading valve seat surface 157a, thereby reducing the contact area with the suction reed valve 157 leading valve seat surface 157a. Can do.

  As a result, the adhesion resistance due to the oil 108 can be reduced, the delay in opening the suction reed valve 157 is reduced, the volumetric efficiency of the compressor is improved, and high efficiency can be realized.

  Therefore, a compressor that achieves both high efficiency and reliability can be realized.

  The suction valve seat surface 155 of the suction valve device 160 has a simple circular configuration for both the outer peripheral shape and the inner peripheral shape, the valve plate 145 is formed of a sintered metal material, and the suction valve seat surface 155 is a sintered mold. Therefore, it is easy to mold the portion that forms the suction valve seat surface 155 of the sintered mold, and the productivity can be improved.

  Further, when the suction valve seat surface 155 is formed on the valve plate 145 by machining or the like, the suction valve seat surface 155 can be formed by using general-purpose equipment such as a lathe or a milling machine, and the equipment investment can be reduced.

  Further, the outer peripheral side and the inner peripheral side of the suction valve seat surface 155 of the suction valve device 160 are provided with R chamfering 163, and therefore the outer peripheral side and inner peripheral side edges of the suction valve seat surface 155 and the suction reed valve 157. Since the contact between the suction reed valve 157 and the suction valve seat surface 155 is changed from line contact to surface contact, the impact load is reduced as the contact area increases, and therefore the suction reed valve 157 is damaged. Can be avoided, and reliability can be improved.

  Furthermore, the refrigerant sealed in the sealed container 101 is a hydrocarbon refrigerant or the like that does not contain chlorine and fluorine, and oil 108 that is compatible with the refrigerant is stored in the sealed container 101.

  As a result, even if the refrigerant dissolves in the oil 108 due to the combination of the oil 108 compatible with the hydrocarbon refrigerant and the oil viscosity decreases, the area of the suction valve seat surface 155 is larger than that of the suction reed valve 157 opposite to the tip side. The distal end side has a larger area, and as a result, the impact load at the portion where the load of the suction reed valve 157 is large is reduced.

  Therefore, high reliability can be obtained.

  Furthermore, the electric element 105 is composed of an inverter-driven motor driven at an arbitrary plurality of operating frequencies such as 70 Hz, and the impact load of the suction reed valve 157 further increases when it is operated at a high speed rotation. The proof strength of 157 becomes severe.

  However, in the present embodiment, the area of the front valve seat surface 157a corresponding to the front end side of the suction reed valve 157 is larger than the area of the anti front end valve seat surface 157b corresponding to the opposite side of the suction reed valve 157. Therefore, the impact load on the distal end side of the suction reed valve 157 is reduced.

  As a result, damage to the suction reed valve 157 can be prevented even at high speed rotation, and operation can be performed without reducing reliability.

  Therefore, it is possible to operate without reducing the reliability even at high speed rotation.

  In the present embodiment, the reciprocating compressor has been described as an example, but it goes without saying that similar actions and effects can be obtained with other compression systems and transfer pumps.

(Embodiment 2)
6 is a cross-sectional view of a compressor according to Embodiment 2 of the present invention, FIG. 7 is a longitudinal cross-sectional view of a discharge valve device according to the same embodiment, and FIG. 8 is a main part of the discharge valve device according to the same embodiment. FIG. 9 is a detailed view, FIG. 9 is a plan view of the discharge valve device according to the embodiment, and FIG. 10 is a plan view of the discharge reed valve of the discharge valve device according to the embodiment.

  6 to 10, the sealed container 201 accommodates an electric element 205 including a stator 203 and a rotor 204 and a compression mechanism 206 driven by the electric element 205.

  The refrigerant sealed in the sealed container 201 is a hydrocarbon refrigerant that does not contain chlorine and fluorine.

  An oil 208 compatible with the refrigerant is stored in the sealed container 201. Oil 208 is a mineral oil that is compatible with a hydrocarbon refrigerant and has a viscosity of 5 to 10 centistokes.

  The suction tube 250 is fixed to the sealed container 201 and connected to the primary side (not shown) of the apparatus, and guides fluid (not shown) into the sealed container 201.

  Next, details of the compression mechanism 206 will be described below.

  The electric element 205 includes a stator 203 and a rotor 204, and is configured by an inverter-driven motor that is driven at an arbitrary plurality of operating frequencies including a rotational speed higher than at least a power supply frequency such as 70 Hz.

  The crankshaft 210 includes a main shaft portion 212 into which the rotor 204 is press-fitted and fixed, and an eccentric portion 213 formed eccentric to the main shaft portion 212.

  A stator 203 is fixed to the cylinder block 215, a substantially cylindrical bore 222 is formed, and a bearing portion 233 that supports the main shaft portion 212 is provided.

  The piston 235 loosely fitted in the bore 222 is connected to the eccentric portion 213 via a piston pin 236 by a connecting rod 240 as a connecting means. The end surface of the bore 222 is sealed with a valve plate 245.

  The head 246 forms a high-pressure chamber and is fixed to the side opposite to the bore 222 of the valve plate 245.

  The suction muffler 252 is sandwiched between the valve plate 245 and the head 246.

  A suction valve device (not shown) is formed on the bore 222 side of the valve plate 245.

  Further, a communication hole 256 is formed in the valve plate 245, and a discharge valve seat surface 280 is formed around the head 246 of the communication hole 256 on the head 246 side, and the discharge valve device 290 is configured together with the discharge reed valve 283. To do. The valve plate 245 is formed of a sintered metal material, and the discharge valve seat surface 280 is formed of a sintered mold.

  The discharge reed valve 283 is made of a leaf spring material, and opens and closes the discharge valve seat surface 280 by elastically deforming one side with the fulcrum portion as a fulcrum.

  The discharge valve seat surface 280 is circular in both outer peripheral shape and inner peripheral shape, and the centers thereof are offset from each other in the longitudinal direction of the discharge reed valve 283. As a result, the area of the front valve seat surface 257a corresponding to the front end side of the discharge reed valve 283 is larger than the area of the anti front valve seat surface 257b corresponding to the opposite side of the discharge reed valve 283.

  In addition, the outer peripheral side and the inner peripheral side of the discharge valve seat surface 280 have R chamfers 263 over the entire circumference.

  About the compressor comprised as mentioned above, the operation | movement and an effect | action are demonstrated below.

  Electric power supplied from a commercial power source (not shown) is supplied to the electric element 205 to rotate the rotor 204 of the electric element 205.

  The rotor 204 rotates the crankshaft 210, and the eccentric movement of the eccentric portion 213 drives the piston 235 from the connecting rod 240 of the connecting means via the piston pin 236, whereby the piston 235 reciprocates in the bore 222, and the suction tube The fluid introduced into the sealed container 201 through 250 is sucked from the suction muffler 252 via a suction valve device (not shown) and continuously compressed in the bore 222.

  This continuously compressed fluid is continuously discharged from the discharge valve device 290 to the high pressure chamber of the head 246. At this time, the discharge reed valve 283 repeatedly opens and closes and continuously collides with the discharge valve seat surface 280.

  At this time, since the opening / closing speed is higher on the distal end side of the discharge reed valve 283, the collision speed to the discharge valve seat surface 280 is also higher.

  However, in the present embodiment, the area of the distal valve seat surface 257a corresponding to the distal end side of the discharge reed valve 283 is larger than the area of the counter distal valve seat surface 257b corresponding to the opposite end side of the discharge reed valve 283. Therefore, since the distal end side of the discharge reed valve 283 is received in a wide area, the impact load generated when the discharge reed valve 283 collides with the distal valve seat surface 257a is reduced and reduced. As a result, the discharge reed valve 283 can be prevented from being damaged.

  On the other hand, by reducing the area of the anti-tip-side valve seat surface 257b of the discharge reed valve 283 having a small impact load from the tip-side valve seat surface 257a, the contact area with the discharge reed valve 283 tip-side valve seat surface 257a can be reduced. Can do.

  As a result, the adhesion resistance due to the oil 208 can be reduced, the delay in opening the discharge reed valve 283 is reduced, the volumetric efficiency of the compressor is improved, and high efficiency can be realized.

  Therefore, a compressor that achieves both high efficiency and reliability can be realized.

  Further, the discharge valve seat surface 280 of the discharge valve device 290 has a simple circular configuration for both the outer peripheral shape and the inner peripheral shape, the valve plate 245 is formed of a sintered metal material, and the discharge valve seat surface 280 is a sintered mold. Therefore, it is easy to mold the portion forming the discharge valve seat surface 280 of the sintered mold, and the productivity can be improved.

  In addition, when the discharge valve seat surface 280 is formed on the valve plate 245 by machining or the like, the discharge valve seat surface 280 can be formed by using general-purpose equipment such as a lathe or a milling machine, so that the equipment investment can be reduced.

  Further, since the outer peripheral side and the inner peripheral side of the discharge valve seat surface 280 of the discharge valve device 290 are provided with R chamfer 263, the outer peripheral side and inner peripheral edge of the discharge valve seat surface 280 and the discharge reed valve 283 are provided. And the contact between the discharge reed valve 283 and the discharge valve seat surface 280 is changed from a line contact to a surface contact, and the impact load is reduced as the contact area increases, so that the discharge reed valve 283 is damaged. Can be avoided, and reliability can be improved.

  Furthermore, the refrigerant sealed in the sealed container 201 is a hydrocarbon refrigerant or the like that does not contain chlorine and fluorine, and the oil 208 that is compatible with the refrigerant is stored in the sealed container 201.

  As a result, even if the refrigerant is dissolved in the oil 208 due to the combination of the oil 208 compatible with the hydrocarbon-based refrigerant and the oil viscosity is lowered, the area of the discharge valve seat surface 280 is larger than that of the discharge reed valve 283 opposite to the tip side. The distal end side has a larger area, and as a result, the impact load at the portion where the load of the discharge reed valve 283 is large is reduced.

  Therefore, high reliability can be obtained.

  Further, the electric element 205 is composed of an inverter-driven motor driven at an arbitrary plurality of operating frequencies such as 70 Hz, and the impact load of the discharge reed valve 283 further increases when operated at a high speed rotation. The proof stress of 283 becomes severe.

  However, in the present embodiment, the area of the distal valve seat surface 257a corresponding to the distal end side of the discharge reed valve 283 is larger than the area of the counter distal valve seat surface 257b corresponding to the opposite end side of the discharge reed valve 283. Therefore, the impact load on the distal end side of the discharge reed valve 283 is reduced.

  As a result, the discharge reed valve 283 can be prevented from being damaged even at high speed rotation, and the operation can be performed without lowering the reliability.

  Therefore, it is possible to operate without reducing the reliability even at high speed rotation.

  In the present embodiment, the reciprocating compressor has been described as an example, but it goes without saying that similar actions and effects can be obtained with other compression systems and transfer pumps.

  As described above, the compressor according to the present invention can be provided with a compressor having high efficiency, low noise, and a long durability life. Therefore, the compressor according to the present invention can be used as a hermetic compressor used in an air conditioner, a refrigerator-freezer, and the like. Is also applicable.

Sectional drawing of the compressor in Embodiment 1 of this invention Vertical sectional view of the suction valve device in the same embodiment Detail drawing of the main part of the intake valve device in the same embodiment Top view of suction valve device in the same embodiment The top view of the suction reed valve of the suction valve device in the same embodiment Sectional drawing of the compressor in Embodiment 2 of this invention Vertical sectional view of the discharge valve device in the same embodiment Detail drawing of the main part of the discharge valve device in the same embodiment The top view of the discharge valve apparatus in the embodiment Top view of the discharge reed valve of the discharge valve device in the same embodiment Cross section of a conventional compressor Exploded perspective view of a conventional valve device

Explanation of symbols

101, 201 Airtight container 106, 206 Compression mechanism 108, 208 Oil 155 Suction valve seat surface 156, 256 Communication hole 157 Suction reed valve 157a, 257a Tip side valve seat surface 157b, 257b Anti-tip side valve seat surface 160 Suction valve device 163 , 263 R chamfer 280 Discharge valve seat surface 283 Discharge reed valve 290 Discharge valve device

Claims (5)

  Oil is stored in a sealed container and a compression mechanism is accommodated, and the compression mechanism includes a valve device that opens and closes by suction and compression strokes, and at least one of the valve devices is formed on a communication hole and an outer periphery of the communication hole. And a cantilevered reed valve that opens and closes the valve seat surface, and the area of the valve seat surface on the distal end side of the reed valve is larger than the area of the valve seat surface on the opposite end side of the reed valve. Larger compressor.   The compressor according to claim 1, wherein both the outer peripheral shape and the inner peripheral shape of the valve seat surface are circular.   The compressor according to claim 1 or 2, wherein an R chamfer is provided on an inner peripheral side of the valve seat surface.   The compressor according to any one of claims 1 to 3, wherein a hydrocarbon refrigerant that does not contain chlorine and fluorine is used as the refrigerant, and oil that is compatible with the refrigerant is used.   The compressor according to any one of claims 1 to 4, wherein the compression element is driven at an operation frequency including a rotational speed higher than at least a power supply frequency.

Images