JP2009047017A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor with a structure which hardly generates stress concentration in an end face member as well as enabling thickness of the end face member to be thin. <P>SOLUTION: The compressor 1 is equipped with a cylinder body 21 forming a cylinder chamber 22, the end face member 23 attached to an end face of the cylinder body 21 and including a discharge hole 23a communicating with the cylinder chamber 22, a discharge valve 31 opening and closing the discharge hole 23a of the end face member 23, a valve pressing member 32 arranged so as to sandwich the discharge valve 31 between itself and the end face member 23, and a fixing bolt 33 for fixing the discharge valve 31 and the valve pressing member 32 to the end face member 23. Then, with a bolt shank 33b of the fixing bolt screwed into a threaded hole 21a formed in the cylinder body 21 while penetrating the valve pressing member 32, the discharge valve 31 and the end face member 23, the valve pressing member 32, the discharge valve 31 and the end face member 23 are supported in a sandwiched manner between a fixing bolt head 33a and the cylinder body 21. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a compressor such as a rotary compressor used in, for example, an air conditioner.

  As shown in FIG. 7, the conventional compressor includes a cylinder upper frame 100 having a discharge hole 100a opened in the cylinder, a discharge valve 101 for opening and closing the discharge hole 100a of the upper frame 100, and the above-described compressor. A valve pressing member 102 that cooperates with the upper frame 100 to sandwich the discharge valve 101 and a fixing bolt 103 are provided.

  The valve pressing member 102 has a through hole 102a, and the upper frame 100 has a screw hole 100b.

  Then, the discharge bolt 101 is inserted into the through hole 102a of the valve pressing member 102 and screwed into the screw hole 100b of the upper frame body 100, whereby the discharge valve 101 is connected to the upper frame body. 100 and the valve pressing member 102 (see Patent Document 1).

  However, in the above conventional compressor, the upper frame 100 has the screw hole 100b, and therefore it is necessary to increase the thickness of the upper frame 100 in order to secure an effective screw length. It was. Therefore, the volume of the discharge hole 100a formed in the upper frame 100 is large.

  Thus, since the volume of the discharge hole 100a is large, the amount of compressed gas remaining in the discharge hole 100a increases at the end of compression, and the compressor is re-expanded by re-expansion of the compressed gas from the discharge hole 100a. The efficiency was lowered and the driving noise was increased.

  More specifically, volumetric efficiency is reduced during low-speed operation of the compressor, and power is increased during high-speed operation of the compressor. Moreover, the pulsation pressure generated by the re-expansion of the compressed gas has increased the operation sound.

  In view of such a problem, in the compressor described in Patent Document 2, as shown in FIG. 8, the fixing bolt 133 is inserted into the through hole 123 b of the end surface member 123 attached to the end surface of the cylinder body 21 and the discharge valve 131. The discharge valve 131 is held between the end face member 123 and the valve pressing member 132 by being inserted into the hole 131 a and screwed into the screw hole 132 a of the valve pressing member 132. Thereby, it is not necessary to form screw holes in the end face member 123, and the thickness of the end face member 123 can be reduced. As a result, the volume of the discharge hole 123a of the end face member 123 is reduced, thereby making it possible to reduce the operation efficiency and prevent the operation sound from increasing.

Japanese Utility Model Publication No. 61-5373 (Fig. 3) JP 2006-189035 A (FIG. 3)

  However, in the compressor disclosed in Patent Document 2, since the head 133a of the fixing bolt 133 is in direct contact with the end surface member 123, the tightening force of the fixing bolt 133 is applied to the head 133a of the end surface member 123. When the thickness of the end face member 123 is reduced by concentrating on the contact portion, the end face member 123 may be distorted.

  Therefore, the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a compressor having a configuration in which the thickness of the end face member can be reduced and stress is not easily concentrated on the end face member. .

  A compressor according to a first aspect of the present invention includes a cylinder body that forms a cylinder chamber, an end surface member that is attached to an end surface of the cylinder body and that communicates with the cylinder chamber, and opens and closes the discharge hole of the end surface member A valve holding member disposed so as to sandwich the discharge valve between the discharge valve and the end surface member, and a fixing bolt for fixing the discharge valve and the valve pressing member to the end surface member The shaft portion of the fixing bolt penetrates through the valve pressing member, the discharge valve, and the end surface member and is screwed into a screw hole formed in the cylinder body. The valve pressing member, the discharge valve, and the end surface member are sandwiched between the head and the cylinder body.

In this compressor, since the fixing bolt is screwed into the screw hole formed in the cylinder body, the length of the screw hole necessary for tightening the fixing bolt is not increased without increasing the thickness of the end face member. Can be secured. As a result, the thickness of the end face member can be reduced.
Further, since the end face member and the head of the fixing bolt are not in direct contact with each other, the fastening force of the fixing bolt acts on the end face member via the valve pressing member and the discharge valve. Thereby, the force which acts on an end surface member is easy to be disperse | distributed, and the stress concentration to an end surface member can be suppressed.

  A compressor according to a second aspect is the compressor according to the first aspect, wherein a contact area between the valve pressing member and the discharge valve is greater than a contact area between the head of the fixing bolt and the valve pressing member. Is also configured to be large.

  In this compressor, by tightening the fixing bolt, the end face member is biased through the discharge valve to an area corresponding to the contact area between the valve pressing member and the discharge valve. Here, since the contact area between the valve pressing member and the discharge valve is larger than the contact area between the head of the fixing bolt and the valve pressing member, compared to the case where the head is directly urged by the head of the fixing bolt, Stress concentration on the end face member can be reliably suppressed.

  A compressor according to a third aspect of the present invention is the compressor according to the first or second aspect, wherein a first chamfered portion is formed at an opening edge portion located on the end surface member side of the screw hole, and the end surface The inner diameter of the first through hole formed in the member and through which the shaft portion of the fixing bolt passes is larger than the diameter of the first chamfered portion at the end surface of the cylinder body.

  In this compressor, due to the processing of the screw hole in the cylinder body, there is a possibility that distortion that protrudes from the surface of the cylinder body occurs at the opening edge of the screw hole, but because the distortion is removed by chamfering, The flatness of the portion in contact with the end face member on the surface of the cylinder body can be increased. Further, since the screw hole is chamfered, distortion that deteriorates the flatness of the surface of the cylinder body when the fixing bolt is screwed is less likely to occur. As a result, it is possible to improve the adhesion between the end face member and the cylinder body and to suppress the end face member from being deformed when the fixing bolt is tightened.

  A compressor according to a fourth aspect is the compressor according to the first or second aspect, wherein the compressor according to the fourth aspect is provided at the opening edge portion of the first through hole located on the cylinder body side. A two-chamfered portion is formed.

  In this compressor, even when a distortion that protrudes from the surface of the cylinder body occurs at the opening edge of the screw hole due to the processing of the screw hole in the cylinder body, the portion of the end face member that faces the distortion is chamfered. Since it is removed, the adhesion between the end face member and the cylinder body does not deteriorate. Further, even when distortion occurs in the vicinity of the screw hole when the fixing bolt is screwed, the adhesion between the end face member and the cylinder body is hardly affected. As a result, it is possible to suppress the end face member from being deformed when the fixing bolt is tightened.

  A compressor according to a fifth aspect of the present invention is the compressor according to the first to fourth aspects of the present invention, wherein the inner diameter of the first through hole is formed in the valve pressing member and the shaft portion of the fixing bolt penetrates the second. It is larger than the inner diameter of the through hole and smaller than the outer diameter of the head of the fixing bolt.

In this compressor, since the inner diameter of the first through hole of the end surface member is larger than the inner diameter of the second through hole formed larger than the inner diameter of the screw hole, the cylinder is formed in the opening facing the cylinder body side in the first through hole. It becomes easy to position the end surface member with respect to the cylinder body so that all the openings of the screw holes of the body are included. As a result, the compressor can be easily assembled.
Further, since the inner diameter of the first through hole is smaller than the outer diameter of the head of the fixing bolt, at least a part of the peripheral portion of the second through hole that is directly urged by the head in the valve pressing member is an end surface. Since it is supported by the member via the discharge valve, it can be configured such that bending stress hardly acts on the peripheral portion of the second through hole of the valve pressing member when the fixing bolt is tightened. As a result, the valve pressing member can be made thin.

  A compressor of a sixth invention is the compressor according to the first to fifth inventions, wherein the end surface member is on a side opposite to the cylinder body side at a position different from the position where the discharge hole is formed. It has a convex part which protrudes toward, and the through-hole for bearings for penetrating and supporting the drive shaft of a compression mechanism is formed in the convex part.

  In this compressor, since the end face member and the bearing of the drive shaft are integrally formed, the number of parts of the compressor can be reduced, and assembly is facilitated. Moreover, the intensity | strength as the whole end surface member can be increased because a convex part is formed in an end surface member. As a result, partial thinning of the end face member is possible.

  A compressor according to a seventh invention is the compressor according to the first to sixth inventions, wherein the end surface member is formed with a recess for accommodating the discharge valve and the valve pressing member, and the discharge hole And the said 1st through-hole is formed in the said hollow part, It is characterized by the above-mentioned.

  In this compressor, since the discharge hole is formed in the hollow portion, the length of the discharge hole can be shortened while ensuring the necessary strength as the entire end face member. Here, for example, when the valve pressing member is fixed at a portion other than the hollow portion and the discharge valve in the hollow portion is pressed by the valve pressing member, it is necessary to form a step or the like on the valve pressing member. The shape of the pressing member becomes complicated. In this regard, in the compressor according to the seventh aspect, since the second through hole and the discharge hole are formed in the hollow portion, the valve pressing member is installed in a state where the valve pressing member is entirely accommodated in the hollow portion. Can do. Thereby, the shape of the valve pressing member can be simplified.

  The compressor according to an eighth aspect of the invention is characterized by being used to compress carbon dioxide used as a refrigerant of the air conditioner while being used in an air conditioner.

  When carbon dioxide is used as a refrigerant in an air conditioner, since the compression ratio is higher than when chlorofluorocarbon or the like is used as a refrigerant, the influence of re-expansion of the refrigerant remaining in the discharge hole is increased. Since this compressor has a structure that can reduce the volume of the discharge hole, the effect of reducing the volume of the discharge hole can be remarkably exhibited by using it in an air conditioner that uses carbon dioxide as a refrigerant.

  As described above, according to the present invention, the following effects can be obtained.

  In the first invention, the length of the screw hole necessary for tightening the fixing bolt can be ensured without increasing the thickness of the end face member. As a result, the thickness of the end face member can be reduced. Further, the force acting on the end face member is easily dispersed by tightening the fixing bolt, and the stress concentration on the end face member can be suppressed.

  In 2nd invention, compared with the case where it is urged | biased directly by the head of a fixing bolt, the stress concentration to an end surface member can be suppressed reliably.

  In 3rd invention, the flatness of the part which contacts the end surface member in the surface of a cylinder main body can be improved. Further, when the fixing bolt is screwed, distortion that deteriorates the flatness of the surface of the cylinder body is less likely to occur.

  In 4th invention, it can suppress that the adhesiveness of an end surface member and a cylinder main body deteriorates. Further, even when distortion occurs in the vicinity of the screw hole when the fixing bolt is screwed, the adhesion between the end face member and the cylinder body is hardly affected.

  In the fifth aspect, it is easy to position the end face member with respect to the cylinder body so that the openings of the first through holes include all the openings of the screw holes of the cylinder body. As a result, the compressor can be easily assembled. Moreover, it can be set as the structure which a bending stress does not act easily to the peripheral part of the 2nd through-hole of a valve pressing member at the time of fastening of a fixing bolt.

  In the sixth invention, the number of parts of the compressor can be reduced, and assembly is facilitated. In addition, since the strength of the end face member as a whole can be increased, partial thinning of the end face member is facilitated.

  In the seventh invention, the length of the discharge hole can be shortened while ensuring the necessary strength for the entire end face member. In addition, since the valve pressing member can be installed in a state in which all the valve pressing members are housed in the recesses, the shape of the valve pressing member can be compared to a configuration in which the valve pressing member is fixed at a portion other than the recesses. It can be simple.

  In the eighth invention, the effect of reducing the volume of the discharge hole can be remarkably exhibited.

  Hereinafter, an embodiment of a compressor according to the present invention will be described based on the drawings.

(First embodiment)
FIG. 1 is a schematic cross-sectional view showing a compressor according to a first embodiment of the present invention. The compressor 1 according to the present invention is a so-called high-pressure dome type rotary compressor, and a compressor 4 is disposed in a casing 4 and a motor 3 is disposed in an upper portion. The compressor 6 is driven by the rotor 6 of the motor 3 via the drive shaft 12.

  The compression unit 2 sucks low-pressure gas (refrigerant) from the accumulator 10 through the suction passage 11. This low-pressure gas is obtained by controlling a condenser, an expansion mechanism, and an evaporator (not shown) constituting an air conditioner as an example of a refrigeration system together with the compressor 1.

  The compressor 1 discharges the compressed high-temperature and high-pressure discharge gas from the compression unit 2 to fill the inside of the casing 4 and cools the motor 3 through the gap between the stator 5 and the rotor 6 of the motor 3. The discharge pipe 13 discharges the outside. Lubricating oil 9 is stored in the lower part of the high pressure region in the casing 4.

  FIG. 2 is a schematic plan view of the cylinder body 21 in FIG. As shown in FIGS. 1 and 2, the compression unit 2 includes a cylinder body 21 that forms a cylinder chamber 22, an upper end surface member 23 that is attached to the upper and lower end surfaces of the cylinder body 21 and covers the cylinder chamber 22, and And a lower end face member 24.

  The upper end face member 23 has a bearing portion 14 (convex portion) formed with a through hole 14a that protrudes toward the side opposite to the cylinder body 21 side and through which the drive shaft 12 is inserted at the center portion. Yes. Similarly, the lower end surface member 24 has a bearing portion 15 that protrudes toward the opposite side of the cylinder body 21 at the center portion and has a through hole 15a through which the drive shaft 12 is inserted. Yes.

  The drive shaft 12 penetrates the through hole 14a of the bearing portion 14 in the end surface member 23 from the motor 3 side and enters the inside of the cylinder chamber 22, and the front end side of the shaft is formed on the lower end surface member 24 of the bearing portion 15. It penetrates through the through hole 15 a and is supported by the bearing portion 14 and the bearing portion 15.

  A roller 27 fitted to a crank pin 26 provided on the drive shaft 12 is disposed in the cylinder chamber 22 so as to be able to revolve, and a compression action is performed by the revolving motion of the roller 27.

  The cylinder chamber 22 is partitioned by a blade 28 provided integrally with the roller 27. That is, as shown in FIG. 2, in the chamber on the right side of the blade 28, the suction passage 11 opens to the inner surface of the cylinder chamber 22 to form a suction chamber 22 a. On the other hand, in the chamber on the left side of the blade 28, a discharge hole 23a shown in FIG. 1 is opened on the inner peripheral surface of the cylinder chamber 22 to form a discharge chamber 22b.

  Semi-circular bushes 25 and 25 are in close contact with both surfaces of the blade 28 for sealing. Lubrication is performed between the blade 28 and the bushes 25 and 25 with the lubricating oil 9.

  The operation of the compression unit 2 will be described. The crank pin 26 rotates eccentrically with the drive shaft 12, and the roller 27 fitted to the crank pin 26 makes the outer peripheral surface of the roller 27 the inner peripheral surface of the cylinder chamber 22. Revolves in contact with the lubricating oil 9.

  As the roller 27 revolves in the cylinder chamber 22, the blade 28 moves forward and backward with both side surfaces of the blade 28 being held by the bushes 25 and 25. Then, a low-pressure refrigerant is sucked into the suction chamber 22a from the suction pipe 11, compressed in the discharge chamber 22b to a high pressure, and then the high-pressure refrigerant is discharged from the discharge hole 23a.

  FIG. 3 is a schematic plan view of the vicinity of the upper end face member 23 in FIG. 4 is a cross-sectional view taken along line XX in FIG. As shown in FIGS. 3 and 4, the end surface member 23 has a hollow portion 23 c that is partially formed thinner than the surroundings. A discharge hole 23a communicating with the cylinder chamber 22 and a through hole 23b (first through hole) penetrating at a position closer to the outer periphery of the end face member 23 than the discharge hole 23a are formed in the hollow portion 23c. Yes.

  A plate-like discharge valve 31 and a plate-like valve pressing member 32 are provided in the recess 23 c in the end surface member 23. The discharge valve 31 opens and closes the discharge hole 23a, and the valve pressing member 32 cooperates with the end surface member 23 to sandwich the discharge valve 31.

  The valve pressing member 32 has a through hole 32a (second through hole) formed with an inner diameter smaller than the inner diameter of the through hole 23b of the end face member 23 and smaller than the outer diameter of the head 33a of the fixing bolt 33. . The outer diameter of the bolt head means the diameter of a circle circumscribing the head if it is a polygonal head. In addition, the discharge valve 31 has a through hole 31 a having substantially the same diameter as the through hole 32 a of the valve pressing member 32. The cylinder body 21 has a screw hole 21a. In order to allow the shaft portion 33b of the fixing bolt 33 having the male screw threaded to pass therethrough, the through hole 32a and the through hole 31a formed in the valve pressing member 32 and the discharge valve 31 are at least of the screw hole 21a. It is formed to have a diameter larger than the inner diameter.

  The discharge valve 31 and the valve pressing member 32 are fixed to the end face member 23 by tightening a fixing bolt 33. That is, the head 33 a of the fixing bolt 33 is disposed on the upper surface side (motor 3 side) of the valve pressing member 32, and the shaft portion 33 b of the fixing bolt 33 is connected to the through hole 32 a of the valve pressing member 32 and the discharge valve 31. The end surface member 23, the discharge valve 31, and the valve pressing member 32 are fixed to the fixing bolt 33 while being inserted into the through hole 31 a and the through hole 23 b of the end surface member 23 and screwed into the screw hole 21 a of the cylinder body 21. Between the head 33a and the cylinder body 21. That is, the discharge valve 31 and the valve pressing member 32 are urged toward the end surface member 23 by the head 33 a of the fixing bolt 33 and are fixed to the end surface member 23. The end face member 23 is fixed to the cylinder body 21 using a plurality of other fixing bolts (not shown).

  The valve pressing member 32 is formed in a flat plate shape in the vicinity of the through hole 32a, and is formed to warp away from the discharge hole 23a in the vicinity of the discharge hole 23a. And the area of the part formed in the flat form of the said valve pressing member 32 is the surface which faces the axial part 33b side in the head 33a of the fixing bolt 33, ie, the biasing surface which can bias the valve pressing member 32. It is formed to be larger than the area. In other words, the contact area between the valve pressing member 32 and the discharge valve 31 is configured to be larger than the contact area between the head 33 a of the fixing bolt 33 and the valve pressing member 32 in a state where the fixing bolt 33 is fixed. Yes.

  The discharge valve 31 closes the discharge hole 23a in the free state. On the other hand, when the refrigerant (compressed gas) in the cylinder chamber 22 becomes larger than the pressure in the muffler chamber 41, the compressed gas is discharged from the discharge hole 23a by elastically deforming the discharge valve 31. The valve pressing member 32 suppresses the movement of the discharge valve 31 so that the discharge valve 31 is not deformed (oscillated) more than necessary.

  As shown in FIG. 1, a cup-type muffler main body 40 is attached to the end surface member 23 so as to cover the discharge valve 31. The muffler main body 40 is fixed to the end surface member 23 by a fixing member such as a bolt.

  A muffler chamber 41 is formed by the muffler body 40 and the end face member 23. The muffler chamber 41 and the cylinder chamber 22 communicate with each other through the discharge hole 23a.

  The muffler main body 40 has a hole 40a. The hole 40 a communicates the muffler chamber 41 with the outside of the muffler main body 40.

  As described above, the compressor 1 includes the cylinder body 21 that forms the cylinder chamber 22, the end face member 23 that is attached to the end face of the cylinder body 21 and that has a discharge hole 23 a communicating with the cylinder chamber 22, and the end face A discharge valve 31 for opening and closing the discharge hole 23a of the member 23, a valve pressing member 32 disposed so as to sandwich the discharge valve 31 between the end face member 23, the discharge valve 31 and the valve pressing member And a fixing bolt 33 for fixing the fixing bolt 33 to the end face member 23, and a shaft portion 33 b of the fixing bolt 33 penetrates the valve pressing member 32, the discharge valve 31, and the end face member 23. The valve retainer between the head 33a of the fixing bolt 33 and the cylinder body 21 while being screwed into the screw hole 21a formed in the cylinder body 21. With product 32 and the discharge valve 31 and the end face member 23 is sandwiched.

  According to this configuration, since the fixing bolt 33 is screwed into the screw hole 21a formed in the cylinder body 21, it is necessary for tightening the fixing bolt 33 without increasing the thickness of the end face member 23. The length of the simple screw hole 21a can be ensured. Thereby, the thickness of the end surface member 23 can be made thin. As a result, the volume of the discharge hole 23a of the end face member 23 can be reduced, and the amount of compressed gas remaining in the discharge hole 23a at the end of compression can be reduced.

  Therefore, it is possible to prevent a decrease in operation efficiency and an increase in operation sound, which are caused by re-expansion of compressed gas from the discharge hole 23a. Specifically, volumetric efficiency can be improved during low speed operation of the compressor, and power can be reduced during high speed operation of the compressor. Further, the pulsation pressure generated by the re-expansion of the compressed gas can be reduced to reduce the operation sound.

  Further, since the fixing bolt 33 and the screw hole 21a of the cylinder body 21 are screw-coupled, the fixing bolt 33 can be retightened as compared with the case where the fixing bolt 33 is fixed with a rivet. The alignment with the hole 23a can be corrected.

  Furthermore, compared with the case where the valve pressing member 32 and the end surface member 23 are fixed with screws and nuts, the number of parts is reduced and the assembly work efficiency is improved.

  In addition, since the end surface member 23 and the head portion 33 a of the fixing bolt 33 are not in direct contact, the fastening force of the fixing bolt 33 acts on the end surface member 23 via the valve pressing member 32 and the discharge valve 31. Thereby, the force acting on the end surface member 23 is easily dispersed, and the stress concentration on the end surface member 23 can be suppressed. Therefore, even if the thickness of the portion of the end face member 23 to which the discharge valve 31 is fixed is reduced, the end face member 23 is only subjected to a small compressive stress. Therefore, the end face member 23 is cast or sintered as a relatively brittle material. Material can be used. Thereby, the end surface member 23 can be manufactured at low cost.

  The compressor is configured such that the contact area between the valve pressing member 32 and the discharge valve 31 is larger than the contact area between the head 33 a of the fixing bolt 33 and the valve pressing member 32. ing.

  According to this configuration, by tightening the fixing bolt 33, the end face member 23 is biased through the discharge valve 31 to an area corresponding to the contact area between the valve pressing member 32 and the discharge valve 31. Here, since the contact area between the valve pressing member 32 and the discharge valve 31 is larger than the contact area between the head 33a of the fixing bolt 33 and the valve pressing member 32, the head 33a of the fixing bolt 33 is directly biased. Compared with the case where it does, the stress concentration to the end surface member 23 can be suppressed reliably.

  In the compressor, the inner diameter of the through hole 23b of the end face member 23 is larger than the inner diameter of the through hole 32a formed in the valve pressing member 32 and through which the shaft portion 33b of the fixing bolt 33 passes, and the fixing bolt 33 It is smaller than the outer diameter of the head 33a.

  According to this configuration, since the inner diameter of the through hole 23b of the end surface member 23 is larger than the inner diameter of the through hole 32a of the valve pressing member 32 formed larger than the inner diameter of the screw hole 21a of the cylinder body 21, It becomes easy to position the end surface member 23 with respect to the cylinder body 21 so that the openings of the through holes 23b facing the cylinder body 21 include all the openings of the screw holes 21a of the cylinder body 21. As a result, the compressor can be easily assembled.

  In addition, the openings of the screw holes 21a are all included in the openings of the through holes 23b, and the screw holes 21a are arranged so as to have a predetermined interval from the opening edges of the screw holes 21a to the opening edges of the through holes 23b. Even when there is distortion or burrs protruding toward the end face member 23 near the opening edge of 21a, the adhesion between the cylinder body 21 and the end face member 23 does not deteriorate.

  Further, the inner diameter of the through hole 32 a of the valve pressing member 32 is formed smaller than the inner diameter of the through hole 23 b of the end face member 23, and the gap between the fixing bolt 33 and the shaft portion 33 b can be reduced. Therefore, the position shift of the valve pressing member 32 can be suppressed.

  Further, since the through hole 32a of the valve pressing member 32 and the through hole 31a of the discharge valve 31 are formed to have substantially the same diameter, the displacement of the discharge valve 31 can also be suppressed.

  The through-hole 32a of the valve pressing member 32 and the through-hole 31a of the discharge valve 31 are formed to have substantially the same diameter and to have a diameter small enough to allow the shaft portion 33b of the fixing bolt 33 to be inserted. By doing so, relative displacement between the valve pressing member 32 and the discharge valve 31 can be suppressed. Further, by forming the recessed portion 23 c along the valve pressing member 32 and the discharge valve 31, it is possible to prevent the valve pressing member and the discharge valve 31 from rotating around the shaft portion 33 b of the fixing bolt 33.

  Further, since the inner diameter of the through hole 23b of the end face member 23 is smaller than the outer diameter of the head 33a of the fixing bolt 33, the peripheral portion of the through hole 23b that is directly biased by the head 33a in the valve pressing member 32. Since at least a part is supported by the end face member 23 via the discharge valve 31, a bending stress is unlikely to act on the peripheral portion of the through hole 32 a of the valve pressing member 32 when the fixing bolt 33 is tightened. it can. As a result, the valve pressing member 32 can be made thin.

  Further, the end face member 23 of the compressor is integrally formed with a bearing portion 14 that protrudes toward the opposite side to the cylinder body 21 side at a position near the recess portion 23c where the discharge hole 23a is formed. Yes. The bearing portion 14 is formed with a through hole 14a (bearing through hole) for penetrating and supporting the drive shaft 12 of the compression mechanism.

  According to this configuration, since the end surface member 23 and the bearing portion 14 of the drive shaft 12 are integrally formed, the number of parts of the compressor can be reduced, and assembly is facilitated. Moreover, the strength of the end face member 23 as a whole can be increased by forming the bearing portion 14 so as to protrude from the surface of the end face member 23. As a result, it is possible to reduce the thickness partially, such as by forming a recess 23c in the end face member 23.

  Further, the end face member 23 of the compressor is formed with a recess 23c for accommodating the discharge valve 31 and the valve pressing member 32, and the discharge hole 23a and the through hole 23b are formed in the recess 23c.

  According to this configuration, since the discharge hole 23a is formed in the hollow portion 23c that is partially formed thin, the discharge hole is secured while ensuring the necessary strength in the end face member 23 in the thick portion other than the hollow portion 23c. The length of 23a can be formed short.

  In addition, when the valve pressing member is fixed at a portion other than the recess 23c and the discharge valve 31 in the recess 23c is pressed by the valve pressing member, it is necessary to process the valve pressing member such as a step. Although the shape of the valve pressing member is complicated, the above-described compressor is configured such that the valve pressing member 32 is entirely accommodated in the recess 23c. 31 can be held.

  The compressor is incorporated in an air conditioner and used for compressing a refrigerant, but is particularly effective as a refrigerant, particularly when carbon dioxide is compressed. Usually, when carbon dioxide is used as a refrigerant, it is necessary to compress at a higher compression ratio than when using chlorofluorocarbon or the like as a refrigerant. For this reason, the influence of re-expansion of the refrigerant remaining in the discharge hole becomes large, which causes a problem. In this regard, in the compressor, since the volume of the discharge hole 23a is small, it is possible to prevent the influence of re-expansion of the refrigerant remaining in the discharge hole 23a from increasing.

(Second Embodiment)
Next, a compressor according to a second embodiment of the present invention will be described. FIG. 5 is an enlarged cross-sectional view of a main part of a compressor according to the second embodiment of the present invention, and is a cross-sectional view of a portion corresponding to FIG. 4 used in the description of the first embodiment. The compressor according to the second embodiment differs from the compressor according to the first embodiment in that the opening edge portion of the screw hole 21a formed in the cylinder body 21 is chamfered. The other parts are the same as those in the first embodiment, and the same members are denoted by the same reference numerals and description thereof is omitted.

  As shown in FIG. 5, the opening edge part of the screw hole 21a formed in the cylinder main body 21 is chamfered, and the taper-shaped chamfer part 21b (1st chamfer part) is formed. The opening diameter of the chamfered portion 21b on the surface of the cylinder body 21 (the maximum diameter of the chamfered portion 21b) is formed to be smaller than the inner diameter of the through hole 23b of the end surface member 23.

  According to this configuration, even if a distortion that protrudes from the surface of the cylinder body 21 occurs at the opening edge of the screw hole 21a due to the processing of the screw hole 21a in the cylinder body 21, the distortion is removed by chamfering. Therefore, the flatness of the portion in contact with the end face member 23 on the surface of the cylinder body 21 can be increased.

  By tightening the fixing bolt in the screw hole, distortion that deteriorates the flatness of the surface of the cylinder body is likely to occur in the vicinity of the opening edge of the screw hole. However, in the configuration of the second embodiment, the opening edge of the screw hole 21a. Since the portion is chamfered, the distortion is less likely to occur when the fixing bolt 33 is screwed together. As a result, the adhesion between the end face member 23 and the cylinder body 21 can be improved.

  Further, since the inner diameter of the through hole 23b formed in the end surface member 23 and through which the shaft portion 33b of the fixing bolt 33 passes is larger than the diameter of the chamfered portion 21b on the end surface of the cylinder body 21, the chamfered portion is formed at the opening of the through hole 23b. It can arrange | position so that all the openings of 21b may be included. Thereby, even if distortion occurs in the vicinity of the chamfered portion 21b, the deformation of the end surface member 23 can be suppressed within the opening of the through hole 23b.

  Further, when the fixing bolt 33 is inserted into the screw hole 21a, the shaft portion 33b of the fixing bolt 33 is aligned by the tapered shape of the chamfered portion 21b, and the shaft portion 33b can be reliably guided to the screw hole 21a.

(Third embodiment)
Next, a compressor according to a third embodiment of the present invention will be described. FIG. 6 is an enlarged cross-sectional view of a main part of a compressor according to the third embodiment of the present invention, and is a cross-sectional view of a portion corresponding to FIG. 4 used in the description of the first embodiment. The compressor according to the third embodiment is different from the compressor according to the first embodiment in that the opening edge portion on the cylinder body 21 side of the through hole 23b formed in the end surface member 23 is chamfered. The other parts are the same as those in the first embodiment, and the same members are denoted by the same reference numerals and description thereof is omitted.

  As shown in FIG. 6, the opening edge of the through hole 23b formed in the end face member 23 on the cylinder body 21 side is chamfered, and a tapered chamfer 23d (second chamfer) is formed.

  According to this configuration, even when a distortion that protrudes from the surface of the cylinder body 21 occurs at the opening edge portion of the screw hole 21 a due to the processing of the screw hole 21 a in the cylinder body 21, the end face member 23 faces the distortion. Since the portion to be removed is removed by chamfering, the adhesion between the end surface member 23 and the cylinder body 21 does not deteriorate.

  Further, even when the fixing bolt 33 is screwed and distortion occurs in the vicinity of the screw hole 21a, the adhesion between the end face member 23 and the cylinder body 21 is hardly affected. As a result, the end face member 23 can be prevented from being deformed when the fixing bolt 33 is tightened.

  Note that the opening edge of the screw hole 21a of the cylinder body 21 may be further chamfered. As a result, the deterioration of the adhesion can be prevented more reliably, and the shaft portion 33b of the fixing bolt 33 can be easily guided to the screw hole 21a.

  As mentioned above, although embodiment of this invention was described based on drawing, it should be thought that a specific structure is not limited to these embodiment. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  In the embodiment, the description has been given by taking the swing type compressor in which the roller 27 and the blade 28 are integrally formed as an example. However, the present invention is not limited to this, and the roller and the blade are configured as separate members. The present invention can also be applied to a rolling piston type compressor. In addition, the present invention can be applied not only to a rotary compressor but also to other types of compressors such as a reciprocator.

  If the present invention is used, the thickness of the end face member can be reduced and the stress can hardly be concentrated on the end face member.

It is a typical sectional view showing the compressor concerning a 1st embodiment of the present invention. It is a typical top view of the cylinder main-body part in FIG. FIG. 2 is a schematic plan view of the vicinity of an upper end face member in FIG. 1. It is XX sectional drawing in FIG. It is a principal part expanded sectional view of the compressor which concerns on 2nd Embodiment of this invention. It is a principal part expanded sectional view of the compressor which concerns on 3rd Embodiment of this invention. It is a principal part expanded sectional view of the conventional compressor. It is a principal part expanded sectional view of the conventional compressor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 12 Drive shaft 14 Bearing part 14a Through-hole 21 Cylinder main body 21a Screw hole 21b Chamfering part (1st chamfering part)
22 Cylinder chamber 23 End face member 23a Discharge hole 23b Through hole (first through hole)
23d Chamfered part (second chamfered part)
23c hollow part 31 discharge valve 31a through hole 32 valve pressing member 32a through hole (second through hole)
33 Fixing bolt 33a Head 33b Shaft

Claims (8)

A cylinder body (21) forming a cylinder chamber (22);
An end face member (23) attached to the end face of the cylinder body and having a discharge hole (23a) communicating with the cylinder chamber;
A discharge valve (31) for opening and closing the discharge hole of the end face member;
A valve pressing member (32) disposed so as to sandwich the discharge valve with the end surface member;
A fixing bolt (33) for fixing the discharge valve and the valve pressing member to the end face member;
With
In the state where the shaft portion (33b) of the fixing bolt penetrates the valve pressing member, the discharge valve, and the end surface member and is screwed into a screw hole (21a) formed in the cylinder body. The compressor is characterized in that the valve pressing member, the discharge valve, and the end face member are sandwiched between the head (33a) of the cylinder and the cylinder body.   The contact area between the valve pressing member and the discharge valve is configured to be larger than the contact area between the head of the fixing bolt and the valve pressing member. Compressor. A first chamfered portion (21b) is formed on the opening edge portion of the screw hole located on the end surface member side,
The inner diameter of the first through hole (23b) formed in the end surface member and through which the shaft portion of the fixing bolt passes is larger than the diameter of the first chamfered portion in the end surface of the cylinder body. The compressor according to claim 1 or 2.   The compressor according to claim 1 or 2, wherein a second chamfered portion (23d) is formed at an opening edge portion of the first through hole located on the cylinder body side.   The inner diameter of the first through hole is larger than the inner diameter of the second through hole (32a) formed in the valve pressing member and through which the shaft portion of the fixing bolt passes, and the outer diameter of the head of the fixing bolt The compressor according to any one of claims 1 to 4, wherein the compressor is smaller than the compressor. The end surface member has a convex portion (14) protruding toward the opposite side to the cylinder body side at a position different from the position where the discharge hole is formed,
6. The through hole for a bearing (14a) for penetrating and supporting the drive shaft (12) of the compression mechanism is formed in the said convex part, The any one of Claim 1 to 5 characterized by the above-mentioned. The compressor according to one item. The end surface member is formed with a recess (23c) for accommodating the discharge valve and the valve pressing member,
The compressor according to any one of claims 1 to 6, wherein the discharge hole and the first through hole are formed in the hollow portion. In addition to being used in air conditioners,
The compressor according to any one of claims 1 to 7, wherein the compressor is used to compress carbon dioxide used as a refrigerant of the air conditioner.

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