JP2011226471A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor which can further reduce power loss and exhibit further excellent durability.SOLUTION: In the compressor, a valve plate 27 and an intake valve plate 25 are provided between a discharge chamber 5b and a compression chamber 24, a discharge port 23b is provided to extend through the valve plate 27 and the intake valve plate 25, and the discharge port 23b is opened and closed by a discharge reed valve 29a. The discharge reed valve 29a includes a fixed part 291a fixed to a fixed surface 27f, a liftable root part 292a extended from the fixed potion 291a to a longitudinal tip side D1, and a valve part 293a extended from the root part 292a to the longitudinal tip side D1 to open and close the discharge port 23b. The valve plate 27 includes a support part 27t for receiving the central area of the valve part 293a, and a receiving part 27h extended from the support part 27t to the longitudinal tip side D1 of the valve part 293a. The receiving part 27h is formed larger than the support part 27t to receive the longitudinal tip side D1 of the valve part 293a.

Description

  The present invention relates to a compressor.

  The following compressors are known (for example, Patent Document 1). In this compressor, a valve plate is provided between the discharge chamber and the compression chamber, and a discharge port that allows communication between the discharge chamber and the compression chamber is provided through the valve plate. The discharge port is opened and closed by a discharge reed valve located in the discharge chamber.

  The discharge reed valve has a fixed portion fixed to a fixed surface that is a surface on the discharge chamber side of the valve plate, a root portion that can be lifted by extending from the fixed portion to the distal end in the longitudinal direction, and a distal end in the longitudinal direction from the root portion. And a valve portion that opens and closes the discharge port. An annular groove surrounding the entire circumference of the discharge port is recessed in the fixed surface. Further, a valve seat surface that is sandwiched between the discharge port and the annular groove and is flush with the outer side of the annular groove is formed on the fixed surface. In the state where the discharge port is closed, the discharge reed valve has a valve portion that exceeds the valve seat surface on the distal end side in the longitudinal direction and protrudes to the annular groove side.

  In this type of compressor, it is ideal to open the discharge port immediately after the difference between the pressure in the discharge chamber and the pressure in the compression chamber exceeds zero. However, when there is lubricating oil as in the actual machine, the contact force S acts in a direction that prevents the opening of the discharge reed valve 81 as shown in FIG. 23, and therefore the force F due to the pressure difference overcomes the contact force S. The discharge reed valve 81 does not open the discharge port 82. At this time, the bore internal pressure of the discharge reed valve is as shown in FIG. The phenomenon in which the bore internal pressure becomes higher than the discharge pressure in this way is called over-compression, which results in power loss. The adhesion is due to the oil film pressure of the lubricating oil. The oil film pressure is more negative than the surrounding pressure when the discharge reed valve 81 is about to leave the valve plate 27. The inventors refer to this action as a “reverse squeeze action”.

Japanese Patent Laid-Open No. 11-117867

  Incidentally, the conventional compressor is required to further reduce power loss from the viewpoint of energy saving.

  Further, in this compressor, there is a concern about the damage of the discharge reed valve, and an improvement in durability is also demanded.

  The present invention has been made in view of the above-described conventional situation, and it is an object to be solved to provide a compressor capable of further reducing power loss and exhibiting superior durability. .

  In order to solve the above-mentioned problems, the inventors focused on the expansion of the discharge port and the moment when the discharge reed valve closes as a result of detailed analysis of the conventional compressor.

  That is, when the discharge port is circular in plan view, for example, the pressure receiving area of the valve portion that opens and closes the discharge port increases in proportion to the square of the diameter of the discharge port. The power to open is increased. On the other hand, in this case, the adhesion force of the lubricating oil that hinders valve opening acts on the peripheral edge of the discharge port, and is therefore only proportional to the diameter of the discharge port. If the discharge port is enlarged, the adhesion force becomes smaller. For this reason, if the discharge port is enlarged, over-compression can be reduced, and power loss can be suppressed.

  However, according to the simulation by the inventors, when the discharge port is enlarged, the central region of the valve portion is an inertial force at the moment when the discharge reed valve is closed, or the pressure difference between the compression chamber and the discharge chamber in the suction process (hereinafter, "It is called" pressure difference "), it is greatly bent in the discharge port, and fatigue failure is likely to occur in the valve portion. This tendency is particularly likely when the compressor is operated at high speed. In this case, the durability of the compressor is reduced.

  In particular, according to the simulation, in the valve portion, the collision with the valve seat surface starts from the root portion side, and a stress wave is propagated toward the tip side. For this reason, when the valve portion of the discharge reed valve is circular in plan view, the valve portion toward the distal end in the longitudinal direction bends like a whip and collides violently with the fixed surface. This is because the weight of the discharge reed valve increases toward the distal end in the longitudinal direction, and a large inertial force acts on the valve portion toward the distal end in the longitudinal direction. This phenomenon is conspicuous when the root portion is a rectangle whose long side extends in the longitudinal direction so that the discharge reed valve opens the discharge port, and the valve portion is a circle whose diameter is the short side of the root portion.

  The inventors have thus completed the present invention.

In the compressor of the present invention, a partition wall is provided between the discharge chamber and the compression chamber, and a discharge port that allows the discharge chamber and the compression chamber to communicate with each other is provided in the partition wall. Opened and closed by a valve
The discharge reed valve includes: a fixed portion fixed to a fixed surface that is a surface of the partition wall on the discharge chamber side; a root portion that extends from the fixed portion to a distal end side in a longitudinal direction; In the compressor comprising a valve portion extending to the distal end side in the longitudinal direction and opening and closing the discharge port,
The partition wall bisects a support portion that supports a central region of the valve portion, a receiving portion that receives a tip region of the valve portion, and a tip discharge region that is the tip side in the longitudinal direction from the support portion. A main connecting portion that extends from the supporting portion and connects the supporting portion and the receiving portion,
The discharge port is provided through the partition wall, leaving the support portion, the receiving portion, and the main connection portion,
The receiving portion is characterized in that a width in a direction perpendicular to the longitudinal direction is formed larger than that of the support portion (Claim 1).

  In the compressor of the present invention, even when the discharge reed valve is closed, the central region of the valve portion is supported by the support portion even if the central region of the valve portion tends to be greatly bent into the discharge port due to inertial force or pressure difference. Further, the support portion, the main connecting portion, and the receiving portion can suitably support the valve portion that collides with the fixed surface while bending like a whip toward the distal end in the longitudinal direction. For this reason, it is hard to produce fatigue failure in a valve part.

  In this compressor, the receiving part is formed so that the width in the direction orthogonal to the longitudinal direction is larger than that of the support part. For this reason, when the valve part of the discharge reed valve collides with the receiving part, the lubricating oil on the receiving part relaxes the collision force due to the squeeze film effect, and only a small stress acts on the valve part. Large stress is unlikely to occur. For this reason, the discharge reed valve is less susceptible to fatigue failure, and the compressor can exhibit high durability. The squeeze film effect is that when the parallel gap decreases at a speed V, the fluid is viscous and resists being pushed out of the gap, generating pressure (proportional to the viscosity coefficient and speed V). It is.

  Under the above action, this compressor increases the pressure receiving area of the valve portion to increase the force for opening the discharge port, and reduces the over-compression by reducing the adhesion force of the lubricating oil that hinders valve opening. It becomes possible to suppress power loss.

  Therefore, the compressor of the present invention can reduce power loss and exhibit more excellent durability.

  Further, in this compressor, since the discharge pulsation can be reduced by suppressing the delay in opening the discharge reed valve, the silence of the compressor can be improved. Furthermore, this compressor tends to reduce excitation force, bearing load, piston side force (lateral force), etc. due to reduction of overcompression, which can reduce mechanical loss and suppress wear. it can. As a result, it is possible to save power and improve reliability.

  Japanese Unexamined Patent Application Publication No. 2009-235913 discloses a compressor provided with a support portion that bisects the entire suction port. However, the present invention has a remarkable effect that the technique disclosed in this document has an excellent effect on the discharge side where more severe performance is required.

  If the width of the support portion, the main connection portion, and the receiving portion is large, fatigue failure of the valve portion is unlikely to occur. On the other hand, if the areas of the support part, the main connection part and the receiving part are increased, the area of the discharge port is reduced, and the contact area of the support part, the main connection part and the receiving part is increased, resulting in an increase in the adhesion force. It is difficult to obtain the effect of opening the port easily. In order to solve these conflicting problems, the present invention can appropriately select the size and shape of the support portion, the main connection portion, and the receiving portion.

  The partition wall may be provided with a sub-connecting portion extending from the support portion so as to at least bisect a base end discharge region which is a base end side in the longitudinal direction from the support portion. And a discharge port may be penetrated by the partition, leaving a support part, a receiving part, a main connection part, and a sub-connection part (Claim 2). In this case, the discharge port is divided into two or more divided ports by the support portion, the receiving portion, the main connecting portion, and the sub connecting portion. In this case, the strength of the support portion is increased, and the valve portion that bends like a whip is easily supported sequentially from the front side in the longitudinal direction toward the front end side, and fatigue failure of the valve portion can be effectively prevented.

  The sub-connecting portion can extend in the longitudinal direction. The discharge port can be divided into two divided ports by the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion (claim 3). In this case, it is easy to realize the effect of preventing the fatigue failure of the valve portion and the opening of the discharge port.

  Further, the width of the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion may increase toward the distal end side in the longitudinal direction (Claim 4). In this case, it is possible to more easily open the discharge port in the proximal discharge region, while the receiving portion more suitably receives the distal end region of the valve portion, thereby further preventing fatigue failure of the valve portion.

  The sub-connecting portion includes a first sub-connecting portion extending in the longitudinal direction, a second sub-connecting portion extending in a direction that forms an angle of 90 ° clockwise with the main connecting portion, and an angle of 90 ° counterclockwise with the main connecting portion. And a third sub-connecting portion extending in a direction of forming The discharge port can be divided into four divided ports by the first sub-connecting portion, the second sub-connecting portion, the third sub-connecting portion, the support portion, the main connecting portion, and the receiving portion. Also in this case, it is easy to realize the effect of preventing the fatigue failure of the valve portion and the opening of the discharge port easily.

  The sub-connecting portion includes a first sub-connecting portion extending in a direction that forms an angle of 120 ° clockwise with the main connecting portion, and a second sub-connecting portion that extends in a direction of forming an angle of 120 ° counterclockwise with the main connecting portion. It can consist of The discharge port can be divided into three divided ports by the first sub-connecting portion, the second sub-connecting portion, the support portion, the main connecting portion, and the receiving portion (claim 6). Also in this case, it is easy to realize the effect of preventing the fatigue failure of the valve portion and the opening of the discharge port easily.

  The sub-connecting portion, the support portion, the main connecting portion, and the receiving portion may be flush with the fixed surface. In this case, the processing cost can be suppressed.

  It is preferable that the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion are formed with recesses that are recessed from the fixed surface. In this case, the contact area between the valve portion of the discharge reed valve and the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion is reduced, and the contact force is reduced and the valve is easily opened.

  The recess is preferably formed in a groove shape in the longitudinal direction (claim 9). In this case, the contact area is reduced, and the close contact force due to the reverse squeeze effect is reduced when the valve is opened, so that the valve is easily opened.

  Moreover, it is also preferable that the recessed part is formed in groove shape in the width direction (Claim 10). This reduces the contact area. In addition, the amount of oil supplied from the fixed surface to the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion is reduced, and the contact force is reduced, making it easier to open the valve.

  It is preferable that crowning is formed in the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion (claim 11). Also in this case, the contact area between the valve portion of the discharge reed valve and the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion is reduced, and the contact force is reduced, thereby facilitating valve opening.

  It is preferable that the valve portion expands in a direction different from the longitudinal direction with respect to the root portion (claim 12). In this case, it is easy to enlarge the discharge port and increase the pressure receiving area of the valve portion. For this reason, it is possible to increase the force for opening the discharge port and to increase the adhesion force of the lubricating oil that prevents the valve opening at the root portion. As a result, overcompression can be further reduced, and power loss can be reliably suppressed. Further, in this case, the tip region of the valve portion is more easily bent like a whip, and violently collides with the fixed surface. For this reason, the effect of a support part, a main connection part, and a receiving part becomes more remarkable.

  When the discharge reed valve with the discharge port closed is viewed in plan, the fixed surface is recessed so as to surround the discharge port and extends to a range overlapping the root portion, the discharge port and the first It is preferable that a valve seat surface sandwiched between the groove portions and flush with the outside of the first groove portion is formed. In this case, the valve portion suitably seals the discharge port by the valve seat surface.

  The first groove is preferably an annular groove surrounding the discharge port in the circumferential direction. In this case, in a state where the discharge reed valve closes the discharge port, the root portion and the circular arc portion facing the proximal end side in the longitudinal direction in the annular groove overlap in a wider range. For this reason, the area where a fixed surface and a root part closely_contact | adhere is reduced by the part of this overlapping area.

  The first groove is preferably a C-shaped groove that surrounds the discharge port in the circumferential direction except for the distal end in the longitudinal direction (claim 15). In this case, the receiving part can be easily formed between them by widening the gap between the opposite ends on the distal end side in the longitudinal direction of the C-shaped groove. For this reason, when the valve part of the discharge reed valve collides with the receiving part, the lubricating oil on the receiving part can surely relieve the collision force, so that only a small stress acts on the valve part, and the tip part of the valve part A large stress is unlikely to occur reliably. As a result, the compressor can effectively prevent the discharge reed valve from being damaged, and can reliably exhibit excellent durability.

  When the discharge reed valve in a state where the discharge port is closed is viewed in plan on the fixed surface, the second groove portion that crosses the root portion in the width direction on the base end side in the longitudinal direction with respect to the discharge port, and a range that overlaps the root portion It is preferable that a communication groove that extends in the longitudinal direction and communicates the first groove portion and the second groove portion is recessed. The portion other than the communication groove on the fixed surface can be a contact portion that contacts the discharge reed valve.

  In this case, when the discharge reed valve closes the discharge port, the second groove portion prevents foreign matter from being caught in the root portion. Further, when the discharge reed valve is opened, a mixed phase jet composed of gas and lubricating oil can blow off the lubricating oil interposed between the root portion and the fixed surface to cut off the oil film. Further, since the jet is discharged from the first groove portion to the outside in the width direction of the discharge reed valve through the communication groove and the second groove portion, the lubricating oil accumulated in the first groove portion can be blown off, and the fixed surface and the root The lubricating oil collected between the two parts and the lubricating oil collected in the second groove part can also be blown off. Further, the area where the fixing surface and the root portion are in close contact with each other is reduced by the communication groove. For this reason, this compressor can advance the timing which a fixed surface and a root part leave | separate, and it becomes difficult to produce gas overcompression.

It is a longitudinal cross-sectional view of the compressor of Example 1. It is a principal part expanded sectional view which shows the state which concerns on the compressor of Example 1 and the discharge reed valve opened the discharge port. FIG. 4 is a plan view showing the valve plate and a discharge valve plate on which a plurality of discharge reed valves are formed according to the compressor of the first embodiment. It is a principal part enlarged plan view which shows the state which concerns on the compressor of Example 1 and the discharge reed valve closed the discharge port. It is a principal part expanded sectional view which concerns on the compressor of Example 1, and shows the state which the discharge reed valve closed the discharge port (the ZZ cross section of FIG. 4 is shown). FIG. 4A is a plan view of a discharge port and the like, FIG. 5B is a plan view of a discharge region, and FIG. FIG. 6 is a plan view of a discharge port and the like according to the compressor of the second embodiment. FIG. 6 is a plan view of a discharge port and the like according to the compressor of Example 3. FIG. 10 is a plan view of a discharge port and the like according to the compressor of the fourth embodiment. FIG. 10 is a cross-sectional view of a support portion corresponding to the line AA in FIG. 6 according to the compressor of Example 5. FIG. 7 is a cross-sectional view of a support portion corresponding to the line BB in FIG. 6 according to the compressor of Example 6. FIG. 10 is a cross-sectional view of a support portion corresponding to the line BB in FIG. 6 according to the compressor of Example 7. FIG. 10 is a cross-sectional view of a support portion corresponding to the line AA in FIG. 6 according to the compressor of Example 8. FIG. 10 is a cross-sectional view of a support portion corresponding to the line AA in FIG. 6 according to the compressor of Example 9. FIG. 10 is a cross-sectional view of a support portion corresponding to the line BB in FIG. 6 according to the compressor of Example 9. FIG. 10A is a plan view of a discharge port and the like, and FIG. It is a principal part enlarged plan view which shows the state which concerns on the compressor of Example 11 and the discharge reed valve closed the discharge port. It is a principal part expanded sectional view which concerns on the compressor of Example 11, and shows the state which the discharge reed valve closed the discharge port (YY cross section of FIG. 17 is shown). It is a principal part enlarged plan view which concerns on the compressor of Example 12 and shows the state which the discharge reed valve closed the discharge port. It is a principal part enlarged plan view which shows the state which concerns on the compressor of Example 13 and the discharge reed valve closed the discharge port. It is a principal part enlarged plan view which concerns on the compressor of Example 14 and shows the state which the discharge reed valve closed the discharge port. FIG. 17 is an enlarged plan view of a main part showing a state where a discharge reed valve closes a discharge port in the compressor of Example 15. It is sectional drawing for demonstrating the contact | adhesion force etc. which act on a discharge reed valve. It is a graph which shows the relationship between the time of a compressor, and a bore | bore internal pressure.

  Hereinafter, Embodiments 1 to 15 embodying the present invention will be described with reference to the drawings.

Example 1
The compressor of the first embodiment is a variable capacity swash plate compressor. In this compressor, as shown in FIG. 1, a plurality of cylinder bores 1a are concentrically formed in a cylinder block 1 in parallel at equal angular intervals. The cylinder block 1 is sandwiched between a front housing 3 positioned at the front and a rear housing 5 positioned at the rear, and is fastened by a plurality of bolts 7 in this state. A crank chamber 9 is formed inside the cylinder block 1 and the front housing 3. The rear housing 5 is formed with a suction chamber 5a and a discharge chamber 5b.

  A shaft hole 3 a is formed in the front housing 3, and a shaft hole 1 b is formed in the cylinder block 1. A drive shaft 11 is rotatably supported in the shaft holes 3a and 1b via a shaft seal device 9a and radial bearings 9b and 9c. A pulley (not shown) or an electromagnetic clutch (not shown) is provided on the drive shaft 11, and a belt (not shown) driven by a vehicle engine is wound around the pulley or the electromagnetic clutch.

  In the crank chamber 9, a lug plate 13 is press-fitted into the drive shaft 11, and a thrust bearing 15 is provided between the lug plate 13 and the front housing 3. A swash plate 17 is inserted through the drive shaft 11. The lug plate 13 and the swash plate 17 are connected by a link mechanism 19 that supports the swash plate 17 so that the tilt angle can be changed.

  A piston 21 is housed in each cylinder bore 1a so as to be able to reciprocate. A valve unit 23 is provided between the cylinder block 1 and the rear housing 5. As shown in an enlarged view in FIG. 2, the valve unit 23 of the compressor includes a suction valve plate 25 that is in contact with the rear end surface of the cylinder block 1, a valve plate 27 that is in contact with the suction valve plate 25, It comprises a discharge valve plate 29 that contacts the valve plate 27 and a retainer plate 31 that contacts the discharge valve plate 29. The retainer 31 also serves as a gasket. The intake valve plate 25, the valve plate 27, the discharge valve plate 29, and the retainer plate 31 are stacked in this order to constitute the valve unit 23.

  As shown in FIG. 1, shoes 33a and 33b that are paired in the front and rear are provided between the swash plate 17 and each piston 21, and the swash plate 17 swings with each pair of shoes 33a and 33b. Each piston 21 is converted into a reciprocating motion.

  The crank chamber 9 and the suction chamber 5a are connected by an extraction passage 35a, and the crank chamber 9 and the discharge chamber 5b are connected by an air supply passage (not shown). A capacity control valve (not shown) is provided in the air supply passage. This capacity control valve can change the opening of the air supply passage in accordance with the suction pressure. A condenser is connected to the discharge chamber 5b of the compressor through a pipe. The condenser is connected to the evaporator through a pipe via an expansion valve. The evaporator is connected to the suction chamber 5a of the compressor through the pipe. Each compression chamber 24 is formed by the cylinder bore 1 a, the piston 21 and the valve unit 23.

  The valve plate 27, the discharge valve plate 29, and the retainer plate 31 are formed with a plurality of suction ports 23a that allow the suction chamber 5a and the compression chambers 24 to communicate with each other. The suction valve plate 25 is formed with a plurality of suction reed valves 25a that open and close the suction ports 23a.

  As shown in FIGS. 2 to 5, the suction valve plate 25 and the valve plate 27 are formed with a plurality of discharge ports 23 b that allow the compression chambers 24 and the discharge chambers 5 b to communicate with each other.

  As shown in FIG. 6A, each discharge port 23b is connected to each of the divided ports 231 and 232 with respect to each cylinder bore 1a by a support part 27t, a receiving part 27h, a main connection part 27v, and a sub-connection part 27w, which will be described later. It is divided.

  As shown in FIG. 2, the discharge valve plate 29 is formed with a plurality of discharge reed valves 29 a that open and close the divided ports 231 and 232. The retainer plate 31 is formed with a retainer 31a that regulates the lift length of each discharge reed valve 29a. In the present embodiment, as shown in FIG. 3, the discharge valve plate 29 has a circular portion and a plurality of extending portions that extend radially outward from the circular portion radially outward. The extended portion is a discharge reed valve 29a, which opens and closes each discharge port 23b.

  As shown in FIGS. 4 to 6, an annular ring groove 27 a that surrounds the discharge port 23 b in the circumferential direction is recessed in the fixed surface 27 f that is the surface on the discharge chamber 5 b side of the valve plate 27. The annular groove 27a is an example of the first groove portion of the present invention. In the fixed surface 27f, an annular region sandwiched between the discharge port 23b and the annular groove 27a is a valve seat surface (also referred to as an eyeglass portion) 27b that is flush with the outside of the annular groove 27a. In this compressor, the suction valve plate 25 and the valve plate 27 are partition walls.

  As shown in FIGS. 2 to 5, the discharge reed valve 29 a includes a fixed portion 291 a fixed to the fixed surface 27 f of the valve plate 27, and six pieces that can be lifted by extending from the fixed portion 291 a to the distal end D 1 in each longitudinal direction. , And six valve portions 293a that open from each root portion 292a to the distal end D1 in the longitudinal direction and open and close each discharge port 23b. In the present embodiment, each longitudinal direction is parallel to the fixed surface 27 f and the radial direction of the drive shaft 11. Each longitudinal tip side D1 is the outside in the radial direction.

  As shown in FIG. 4, when the root portion 292a and the valve portion 293a are viewed in plan, the root portion 292a has a rectangular shape whose long side extends to the distal end side D1 in the longitudinal direction. The valve portion 293a has a short side of the root portion 292a as a diameter, and has a circular shape concentric with the annular groove 27a. The diameter of the valve portion 293a in the direction orthogonal to the distal end side D1 in the longitudinal direction is larger than the diameter of the distal end side D1 in the longitudinal direction of the valve seat surface 27b.

  As shown in FIGS. 4 and 6, the valve plate 27 includes a support portion 27t that receives the central region of the valve portion 293a, a receiving portion 27h that receives the tip region of the valve portion 293a, a support portion 27t, and a receiving portion 27. A main connecting portion 27v for connecting the two and a sub-connecting portion 27w extending from the support portion 27t are set. The central region of the valve portion 293a is a certain range including the center since the valve portion 293a is circular. The tip region of the valve portion 293a is a certain range located on the tip side D1 from the central region. As shown in FIG. 6B, the valve plate 27 is provided with a discharge region A in which a discharge port 23b is provided on the inner side. The discharge area A is composed of a semicircular tip discharge area A1 located on the distal end side D1 in the longitudinal direction and a semicircular proximal discharge area A2 located on the proximal end side D2 in the longitudinal direction. As shown in FIG. 6A, the support portion 27t is a certain range including the center O of the ejection region A. The support part 27t is positioned so as to receive the central region of the valve part 293a, and discharge ports 23b exist on the left and right of the distal end side D1 and the left and right of the base end side D2 in the longitudinal direction when viewed from the support part 27t. The main connecting portion 27v extends from the support portion 27t so as to bisect the tip discharge area A1 from the support portion 27t. The sub-linking part 27w bisects the proximal discharge area A2 from the support part 27t. The valve plate 27 is provided with a discharge port 23b, leaving the support portion 27t, the receiving portion 27h, the main connection portion 27v, and the sub-connection portion 27w. Since the valve plate 27 is provided with the support portion 27t, the receiving portion 27h, the main connecting portion 27v, and the sub connecting portion 27w, the discharge port 23b is divided into two divided ports 231 and 232.

  The sub-connecting portion 27w, the support portion 27t, the main connecting portion 27v, and the receiving portion 27h have an I-shape that extends to the distal end side D1 in the longitudinal direction. As shown in FIG. 6C, the support portion 27t, the receiving portion 27h, the main connecting portion 27v, and the sub connecting portion 27w are flush with the fixed surface 27f. Between the divided ports 231 and 232, a support portion 27t, a receiving portion 27h, a main connection portion 27v, and a sub connection portion 27w exist. The divided ports 231 and 232 having such a shape are formed by punching and pressing the valve plate 27, for example.

  As shown in FIG. 6A, the support portion 27t, the main connection portion 27v, and the sub-connection portion 27w have the same width in the direction orthogonal to the longitudinal direction, but the receiving portion 27h has the width of the support portion 27t and the main connection portion 27v. And it is formed larger than the sub coupling part 27w. Note that the corners of the divided ports 231 and 232 are slightly rounded, not pin angles, due to processing accuracy limitations such as punching press processing.

  As shown in FIGS. 2 to 5, a long groove 27 c is formed in the fixing surface 27 f so as to straddle the root portion 292 a in the width direction on the base end side D <b> 2 in the longitudinal direction with respect to the discharge port 23 b. The long groove 27c is an example of the second groove portion of the present invention. As shown in FIG. 4, when the long groove 27c is viewed in plan, the shape of the long groove 27c is an elongated oval shape orthogonal to the distal end side D1 in the longitudinal direction. The long groove 27c is formed deeper than the annular groove 27a.

  In the compressor configured as described above, when the drive shaft 11 is rotationally driven, the lug plate 13 and the swash plate 17 rotate synchronously with the drive shaft 11, and each stroke is performed according to the inclination angle of the swash plate 17. The piston 21 reciprocates in each cylinder bore 1a. For this reason, the refrigerant gas in the suction chamber 5a is sucked into each compression chamber 24, compressed, and discharged into the discharge chamber 5b. The refrigerant gas that is compressed by the compressor contains mist-like lubricating oil. This lubricating oil is interposed in sliding portions such as the pistons 21, the shoes 33a and 33b, the swash plate 17, and the like to suppress wear. Lubricating oil also accumulates in the annular groove 27a and the long groove 27c.

  During this time, as shown in FIG. 2, due to the difference between the pressure in the discharge chamber 5b and the pressure in the compression chamber 24, the discharge reed valve 29a is elastically deformed at the root portion 292a and the discharge port 23b is opened at the valve portion 293a. As shown in FIG. 5, the valve portion 293a does not open the discharge port 23b until the pressure difference overcomes the adhesion force of the root portion 292a.

  In this compressor, even when the discharge reed valve 29a is closed, the central region of the valve portion 293a is supported by the support portion 27t even if the central region of the valve portion 293a tends to be greatly bent into the discharge port 23b due to inertial force or pressure difference. Is done. Further, since the sub-connecting portion 27w, the supporting portion 27t, the main connecting portion 27v, and the receiving portion 27h are formed in an I shape extending to the distal end side D1 in the longitudinal direction, the strength of the supporting portion 27t increases and the longitudinal direction The valve portion 293a that collides with the fixed surface 27f while being bent like a whip toward the distal end side D1 is easily and favorably supported sequentially from the front side in the longitudinal direction toward the distal end side D1. For this reason, it is hard to produce fatigue failure in the valve part 293a.

  In particular, in this compressor, when the valve portion 293a of the discharge reed valve 29a collides with the receiving portion 27h, the lubricating oil on the receiving portion 27h relaxes the collision force by the squeeze film effect, and only a small stress acts on the valve portion 293a. Therefore, a large stress is hardly generated at the tip of the valve portion 293a. For this reason, the discharge reed valve 29a is less susceptible to fatigue failure, and the compressor can exhibit high durability.

  In this compressor, under the above-described action, the pressure receiving area of the valve portion 293a is increased to increase the force for opening the discharge port 23b, and by reducing the contact force of the lubricating oil that hinders the valve opening, It becomes possible to reduce, and it becomes possible to suppress power loss.

  Therefore, the compressor can further reduce power loss and exhibit more excellent durability.

  Further, in this compressor, since the discharge pulsation can be reduced by suppressing the delay in opening of the discharge reed valve 29a, the silence of the compressor can be improved. Furthermore, in this compressor, since the peak pressure in the compression chamber 24 can be reduced, the maximum compression load is reduced, the thrust bearing 15, the seating surfaces of the shoes 33a, 33b and the piston 21, the shoes 33a, 33b and the swash plate 17 are reduced. This increases the reliability of the sliding surface.

  Further, in this compressor, as shown in FIG. 4, an annular groove 27 a is recessed in the fixed surface 27 f of the valve plate 27. Therefore, in a state where the discharge reed valve 29a closes the discharge port 23b, the root portion 292a and the arc portion 27g (shown in FIG. 4) facing the longitudinal base end side D2 in the annular groove 27a are in a wide range. Overlap. For this reason, the area where the fixing surface 27f and the root portion 292a are in close contact with each other is reduced by the overlapping area. For this reason, the opening delay of the discharge reed valve 29a can be reduced.

  Further, in this compressor, a long groove 27c is recessed in the fixed surface 27f. For this reason, in a state where the discharge reed valve 29a closes the discharge port 23b, foreign matter is prevented from being caught in the root portion 292a.

(Example 2)
As shown in FIG. 7, the compressor of the second embodiment has a discharge port 23 b formed by combining four fan-shaped divided ports 231 to 234 having a central angle of about 90 degrees.

  The valve plate 27 includes a support portion 27d, a main connection portion 27v, a receiving portion 27h, and first to third sub-connection portions 27w1 to 27w3. The first sub connecting portion 27w1 extends in the longitudinal direction. The second sub-connecting portion 27w2 extends in a direction that forms a 90 ° clockwise angle with the main connecting portion 27v. The third sub-connecting portion 27w3 extends in a direction that forms an angle of 90 ° counterclockwise with the main connecting portion 27v. Between the divided ports 231 to 234, a support portion 27d, a main connection portion 27v, a receiving portion 27h, and first to third sub-connection portions 27w1 to 27w3 exist. Other configurations are the same as those of the compressor of the first embodiment.

  Also in this compressor, the same operation effect as the compressor of Example 1 can be produced.

(Example 3)
As shown in FIG. 8, the compressor of the third embodiment has a discharge port 23 b configured by combining three fan-shaped divided ports 231 to 233 having a central angle of about 120 degrees.

  The valve plate 27 is formed with a support portion 27e, a main connection portion 27v, a receiving portion 27h, and first and second sub-connection portions 27w1 and 27w2. The first sub-connecting portion 27w1 extends in a direction that forms an angle of 120 ° clockwise with the main connecting portion 27v. The second sub-connecting portion 27w2 extends in a direction that forms an angle of 120 ° counterclockwise with the main connecting portion 27v. Between the divided ports 231 to 233, there are a support portion 27e, a main connection portion 27v, a receiving portion 27h, and first and second sub-connection portions 27w1 and 27w2. Other configurations are the same as those of the compressor of the first embodiment.

  Also in this compressor, the same operation effect as the compressor of Example 1 can be produced.

Example 4
As shown in FIG. 9, the compressor of the fourth embodiment employs half-moon shaped divided ports 231 and 232. Further, the width of the sub-connecting portion 27w, the support portion 27i, the main connecting portion 27v, and the receiving portion 27j is increased toward the distal end side D1 in the longitudinal direction. Other configurations are the same as those of the compressor of the first embodiment.

  Also in this compressor, the same operation effect as the compressor of Example 1 can be produced.

  According to the present invention, the large deflection of the central region of the valve portion 293a into the discharge port 23b can be greatly reduced. For this reason, the valve part 293a does not necessarily need to contact over the whole support part, receiving part, main connection part, and sub-connection part. For this reason, the form of the following Examples 5-10 may also be employ | adopted.

(Example 5)
In the compressor according to the fifth embodiment, as shown in FIG. 10, a recess 27k is formed on the surface of the support portion 27t or the like. The recess 27k is formed in a groove shape at both ends in the width direction such as the support portion 27t. Other configurations are the same as those of the compressor of the first embodiment.

  In this compressor, the contact area between the valve portion 293a of the discharge reed valve 29a and the support portion 27t is reduced, and the contact force is reduced and the valve is easily opened. Further, with this structure, it is possible to suppress the contact area and hence the adhesion force while maintaining the strength by giving the support portion 27t a width. Other functions and effects are the same as those of the first embodiment.

(Example 6)
In the compressor according to the sixth embodiment, as shown in FIG. 11, a recess 28a is provided on the surface of the support portion 27t or the like. The recess 28a is formed in a groove shape in the length direction of the support portion 27t and the like. Other configurations are the same as those of the compressor of the first embodiment.

  In this compressor, the contact area is reduced, and the contact force due to the reverse squeeze effect is reduced when the valve is opened, so that the valve is easily opened. Other functions and effects are the same as those of the first embodiment.

(Example 7)
In the compressor of the seventh embodiment, as shown in FIG. 12, narrow groove-shaped recesses 27m are formed at both ends in the length direction of the support portion 27t and the like. Other configurations are the same as those of the compressor of the first embodiment.

  In this compressor, since the recess 27m cuts off the lubricant oil between the valve seat surface 27b and the support portion 27t, the supply of the lubricant oil from the valve seat surface 27b to the support portion 27t is cut off. The contact force acting between the support portion 27t and the like and the valve portion 293a is reduced, and the valve is easily opened. Other functions and effects are the same as those of the first embodiment.

(Example 8)
In the compressor of Example 8, as shown in FIG. 13, together with the concave portions 27s at both ends, three thin groove-shaped concave portions 27n positioned between them are formed in the support portion 27t and the like. Other configurations are the same as those of the compressor of the sixth embodiment.

  In this compressor, the contact area between the support part 27t and the like and the valve part 293a is reduced, the contact force is reduced, and the valve is easily opened. Other functions and effects are the same as those of the first embodiment.

Example 9
In the compressor of the ninth embodiment, as shown in FIG. 14 or FIG. 15, a crowning 27p is formed on the support portion 27t and the like. Other configurations are the same as those of the compressor of the first embodiment.

  Also in this compressor, the contact area between the valve part 293a of the discharge reed valve 29a and the support part 27t becomes small, the contact force becomes small, and the valve is easily opened. Other functions and effects are the same as those of the first embodiment.

(Example 10)
In the compressor of the tenth embodiment, as shown in FIG. 16, a plurality of recesses 27q are formed by performing coining on the support portion 27t and the like and then grinding. Other configurations are the same as those of the compressor of the first embodiment. This compressor can achieve the same effects as the compressor of the sixth embodiment.

(Example 11)
In the compressor of the eleventh embodiment, as shown in FIGS. 17 and 18, a communication groove 27r is formed on the fixed surface 27f so as to extend to the distal end side D1 in the longitudinal direction and communicate the annular groove 27a and the long groove 27c. A portion of the fixed surface 27f other than the communication groove 27r serves as a contact portion 27s that contacts the discharge reed valve 29a. The contact portion 27s is positioned on both sides in the width direction of the communication groove 27r on the fixed surface 27f, and overlaps the root portion 292a when the discharge reed valve 29a with the discharge port 23b closed is viewed in plan view. In this embodiment, the width of the communication groove 27r is about 50% to 75% with respect to the width of the root portion 292a, so that the contact portion 27s can reliably support the root portion 292a.

  In this compressor, when the discharge reed valve 29a is opened, the mixed phase jet composed of the refrigerant gas and the lubricating oil can blow off the lubricating oil interposed between the root portion 292a and the fixed surface 27f to cut off the oil film. Further, since the jet is discharged from the annular groove 27a to the outer side in the width direction of the discharge reed valve 29a through the communication groove 27r and the long groove 27c, the lubricating oil accumulated in the annular groove 27a can be blown off and the fixed surface 27f It is possible to blow off the lubricating oil collected between the base portion 292a and the lubricating oil collected in the long groove 27c. Further, the area where the fixing surface 27f and the root portion 292a are in close contact with each other is reduced by the communication groove 27r. For this reason, this compressor can advance the timing which the fixed surface 27f and the root part 292a space apart, and it becomes difficult to produce overcompression of refrigerant gas. Other functions and effects are the same as those of the first embodiment.

(Example 12)
In the compressor of the twelfth embodiment, as shown in FIG. 19, the valve portion 293a has a circular shape with a diameter equal to or longer than the short side of the root portion 292a. That is, the valve portion 293a extends in a direction different from the distal end side D1 in the longitudinal direction with respect to the root portion 292a. Other configurations are the same as those of the first embodiment.

  In this case, it is possible to easily increase the discharge port 23b and increase the pressure receiving area of the valve portion 293a. Therefore, it is possible to increase the force for opening the discharge port 23b and to avoid an increase in the adhesion force of the lubricating oil that prevents the valve opening at the root portion 292a. As a result, overcompression can be further reduced, and power loss can be reliably suppressed. In this case, the tip of the valve portion 293a toward the tip end D1 in the longitudinal direction is more likely to be bent like a whip, and violently collides with the fixed surface 27f. For this reason, the effect of the support portion 27t and the like becomes more prominent. Other functions and effects are the same as those of the first embodiment.

(Example 13)
In the compressor of Example 13, as shown in FIG. 20, instead of the support part 27t of Example 1, the support part 27i of Example 4 is adopted, and instead of the annular groove 27a of Example 1, A C-shaped groove 27c is employed. The C-shaped groove 27c is also an example of the first groove portion of the present invention. The C-shaped groove 27c is recessed in an arc shape concentric with the center O on the fixed surface 27f, and surrounds the discharge port 23b in the circumferential direction except for the distal end side of the distal end side D1 in the longitudinal direction. In the fixed surface 27f, the region sandwiched between the opposite ends of the C-shaped groove 27y on the distal end side of the longitudinal distal end side D1 is a receiving portion 27z together with the receiving portion 27j. Other configurations are the same as those of the first embodiment.

  In this case, the distance between both ends facing each other on the distal end side of the distal end side D1 in the longitudinal direction of the C-shaped groove 27y is increased to be larger in the width direction of the support portion 27i than the other portions of the support portion 27i. The received receiving portions 27j and 27z can be easily formed. For this reason, when the valve portion 293a collides with the receiving portions 27j, 27z, the lubricating oil on the large receiving portions 27j, 27z can reliably relieve the collision force, so that only a small stress acts on the valve portion 293a, and the valve It is difficult for a large stress to occur reliably at the tip of the portion 293a. As a result, the compressor can effectively prevent the discharge reed valve 29a from being damaged, and can reliably exhibit excellent durability. Other functions and effects are the same as those of the first embodiment.

(Example 14)
In the compressor of Example 14, as shown in FIG. 21, instead of the support part 27t of Example 1, the support part 27i of Example 4 is adopted, and instead of the annular groove 27a of Example 1, A pair of first groove portions 27x is employed. Both the first groove portions 27x are recessed in an arc shape concentric with the center O on the fixed surface 27f, and surround the discharge port 23b from the left and right except for the distal end side D1 and the proximal end side D2 in the longitudinal direction. In the fixed surface 27f, a region sandwiched between the ends facing each other on the distal end side D1 in the longitudinal direction in both first groove portions 27x is a receiving portion 27z together with the receiving portion 27j. On the other hand, in the fixed surface 27f, a region sandwiched between ends facing each other on the base end side D2 in the longitudinal direction in both first groove portions 27x is a base end side receiving portion 274. Other configurations are the same as those of the first embodiment.

  In this case, the receiving portions 27j and 27z larger than the other portions can be easily formed between the first groove portions 27x by widening the distance between the opposing end portions on the front end side D1 in the longitudinal direction. For this reason, similarly to the compressor of the thirteenth embodiment, it is difficult to reliably generate a large stress at the tip of the valve portion 293a. Further, in this compressor, when the base portion 292a of the discharge reed valve 29a collides with the base end side receiving portion 274, only a small stress acts on the base portion 292a by the large base end side receiving portion 274. As a result, the compressor can effectively prevent the discharge reed valve 29a from being damaged, and can reliably exhibit excellent durability. Other functions and effects are the same as those of the first embodiment.

(Example 15)
In the compressor of the fifteenth embodiment, as shown in FIG. 22, the valve plate 27 is provided with only the support portion 27u, the main coupling portion 27v, and the receiving portion 27h, and the U-shaped discharge port 23b is employed. For this reason, the support part 27u can receive the center area | region of the valve part 293a similarly to the support part 27t. Other configurations are the same as those of the first embodiment.

  Also in this case, the same effects as those of the first embodiment can be achieved.

  In the above, the present invention has been described with reference to the first to fifteenth embodiments. However, the present invention is not limited to the first to fifteenth embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, a support part etc. may be formed in the valve plate 27, and may be formed in other members, such as a damping steel plate.

  In the first embodiment, the long groove 27c is formed deeper than the annular groove 27a. In the eleventh embodiment, the annular groove 27a, the long groove 27c, and the communication groove 27r are formed at the same depth. However, these depths are not limited thereto. It is not something.

  The recesses 27k, 27a, 27m, 27s, 27q, and the crowning 27p described in Examples 5 to 10 may be provided only in the support portion 27t, and the support portion 27t, the main connection portion 27v, and the sub-connection portions 27w, 27w1 to 27w3. It may be provided across.

  The present invention is applicable to a vehicle air conditioner.

5b ... discharge chamber, 24 ... compression chamber 25, 27 ... partition wall (25 ... suction valve plate, 27 ... valve plate)
23b ... Discharge port 231-234 ... Divided port 29a ... Discharge reed valve 27f ... Fixed surface 291a ... Fixed part D1 ... Longitudinal tip 292a ... Root part 293a ... Valve part 27t, 27d, 27e, 27i, 27u ... Support part 27h ... receiving portion 27v ... main connecting portion 27w, 27w1-3 ... sub connecting portion 27k, 27m, 27n, 27q, 28a, 27s ... concave portion 27p ... crowning 27a, 27x, 27y ... first groove portion (27a ... annular groove, 27y ... C-shaped groove)
27b ... Valve seat surface 27h, 27j, 27z ... Receiving portion 27c ... Second groove (long groove)
27r ... Communication groove

Claims (16)

A partition is provided between the discharge chamber and the compression chamber, and a discharge port that allows the discharge chamber and the compression chamber to communicate with each other is penetrated through the partition, and the discharge port is opened and closed by a discharge reed valve,
The discharge reed valve includes: a fixed portion fixed to a fixed surface that is a surface of the partition wall on the discharge chamber side; a root portion that extends from the fixed portion to a distal end side in a longitudinal direction; In the compressor comprising a valve portion extending to the distal end side in the longitudinal direction and opening and closing the discharge port,
The partition wall bisects a support portion that supports a central region of the valve portion, a receiving portion that receives a tip region of the valve portion, and a tip discharge region that is the tip side in the longitudinal direction from the support portion. And a main connecting portion extending from the support portion and connecting the support portion and the receiving portion is set.
The discharge port is provided through the partition wall, leaving the support portion, the receiving portion, and the main connection portion,
The compressor is characterized in that the receiving portion is formed to have a width in a direction perpendicular to the longitudinal direction larger than that of the support portion. In the partition, a sub-connecting portion extending from the support portion is set so as to at least bisect a base end discharge region which is a base end side in the longitudinal direction from the support portion,
2. The compressor according to claim 1, wherein the discharge port is provided through the partition wall, leaving the support portion, the receiving portion, the main connection portion, and the sub-connection portion. The sub-connecting portion extends in the longitudinal direction;
The compressor according to claim 2, wherein the discharge port is divided into two divided ports by the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.   The compressor according to claim 3, wherein the width of the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion is widened toward the distal end side in the longitudinal direction. The sub-connecting portion includes a first sub-connecting portion extending in the longitudinal direction, a second sub-connecting portion extending in a direction that forms an angle of 90 ° clockwise with the main connecting portion, and a counterclockwise rotation with the main connecting portion. A third sub-connecting portion extending in a direction forming an angle of 90 °,
The discharge port is divided into four divided ports by the first sub-connecting portion, the second sub-connecting portion, the third sub-connecting portion, the support portion, the main connecting portion, and the receiving portion. Item 3. The compressor according to Item 2. The sub-connecting portion includes a first sub-connecting portion extending in a direction that forms an angle of 120 ° clockwise with the main connecting portion, and a second sub-connecting portion that extends in a direction of forming an angle of 120 ° counterclockwise with the main connecting portion. It consists of a connecting part,
The compressor according to claim 2, wherein the discharge port is divided into three divided ports by the first sub-connecting portion, the second sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.   The compressor according to claim 2, wherein the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion are flush with the fixed surface.   The compressor according to claim 2, wherein the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion are formed with recesses that are recessed from the fixed surface.   The compressor according to claim 8, wherein the recess is formed in a groove shape in the longitudinal direction.   The compressor according to claim 8, wherein the recess is formed in a groove shape in the width direction.   The compressor according to claim 2, wherein a crowning is formed in the sub-connecting portion, the support portion, the main connecting portion, and the receiving portion.   The compressor according to any one of claims 1 to 11, wherein the valve portion extends in a direction different from the longitudinal direction with respect to the root portion.   When the discharge reed valve in a state in which the discharge port is closed is viewed in plan on the fixed surface, a first groove portion that is recessed so as to surround the discharge port and extends to a range overlapping the root portion, The compressor according to any one of claims 1 to 12, wherein a valve seat surface sandwiched between the discharge port and the first groove portion and flush with the outside of the first groove portion is formed.   The compressor according to claim 13, wherein the first groove portion is an annular groove surrounding the discharge port in the circumferential direction.   The compressor according to claim 13, wherein the first groove portion is a C-shaped groove that surrounds the discharge port in a circumferential direction except for the distal end side in the longitudinal direction.   In the fixed surface, when the discharge reed valve in a state where the discharge port is closed is viewed in plan, a second groove portion straddling the base portion in the width direction on the base end side in the longitudinal direction with respect to the discharge port The compression groove according to any one of claims 13 to 15, wherein a communication groove that extends in the longitudinal direction in a range overlapping with the root portion and communicates the first groove portion and the second groove portion is recessed. Machine.

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