JP2006189035A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor improving performance by reducing the volume of a discharge hole. <P>SOLUTION: A fixation bolt 33 is inserted through a through-hole 23b of an end face member 23 and screwed into a screw hole 32a of a valve pressing member 32, and by this, a discharge valve 31 is sandwiched between the end face member 23 and the valve pressing member 32. Since the thickness of the end face member 23 can be reduced, the volume of the discharge hole 23a of the end surface member 23 can be reduced to prevent a decrease in operation efficiency and an increase in operation sound. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

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

  As shown in FIG. 10, a 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 Japanese Utility Model Laid-Open No. 61-5373: 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. For this reason, the axial direction (thickness direction) dimension of the screw hole 100b of the upper frame 100 is increased, and the volume of the screw hole 100b of the upper frame 100 (hereinafter referred to as top clearance) is increased. It was.

  Thus, since the top clearance is large, the amount of compressed gas remaining in the discharge hole 100a at the end of compression increases, and the compressor is generated by re-expansion of the compressed gas from the discharge hole 100a. Reduced the efficiency and driving noise.

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.
Japanese Utility Model Publication No. 61-5373 (Fig. 3)

  SUMMARY OF THE INVENTION An object of the present invention is to provide a compressor with improved performance by reducing the volume of a discharge hole.

In order to solve the above problems, the compressor of the present invention is:
A cylinder body forming a cylinder chamber;
An end face member attached to the end face of the cylinder body and having a discharge hole and a through hole communicating with the cylinder chamber;
A discharge valve for opening and closing the discharge hole of the end face member;
A valve pressing member that cooperates with the end face member to sandwich the discharge valve and has a screw hole;
A fixing bolt having a head,
The head of the fixing bolt is disposed on the cylinder body side of the end surface member, and the fixing bolt is inserted into the through hole of the end surface member and screwed into the screw hole of the valve pressing member. In this state, the discharge valve is sandwiched between the end face member and the valve pressing member.

  According to the compressor of the present invention, the fixing bolt is inserted into the through hole of the end surface member and screwed into the screw hole of the valve pressing member, and the discharge valve is connected to the end surface member. Therefore, it is not necessary to cut a screw in the through hole of the end face member, and the thickness of the end face member around the through hole can be reduced. That is, the dimension in the axial direction (thickness direction) of the discharge hole of the end face member can be reduced.

  Thus, the volume (space) of the discharge hole of the end face member can be reduced, and the amount of compressed gas remaining in the discharge hole 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 the compressed gas from the inside of the discharge hole. 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.

  Of course, since the fixing bolt and the screw hole of the valve pressing member are screw-coupled, the fixing bolt is compared with the case where the valve pressing member and the end surface member are fixed with a rivet. Can be retightened, and the alignment of the discharge valve and the discharge hole can be corrected. Furthermore, compared with the case where the said valve holding member and the said end surface member are fixed with a screw and a nut, the number of parts reduces and the working efficiency of an assembly improves.

  Moreover, in the compressor of one Embodiment, the said cylinder main body has a recessed part which accommodates the said head of the said fixing bolt in the end surface of this cylinder main body.

  According to the compressor of this embodiment, the cylinder body has a recess for accommodating the head portion of the fixing bolt on the end surface of the cylinder body, so that the head portion of the fixing bolt is connected to the cylinder body. It can hide in the said recessed part of an end surface. Thus, since the fixing bolt can be arranged avoiding the cylinder chamber (compression chamber), the through hole of the end surface member through which the fixing bolt is inserted does not serve as a bypass passage of the cylinder chamber, and is compressed. There is no performance degradation.

  Moreover, in the compressor of one Embodiment, the said screw hole of the said valve pressing member is given the burring process.

  According to the compressor of this embodiment, since the screw hole of the valve pressing member is subjected to burring, an effective screw length can be secured without increasing the thickness of the valve pressing member. Further, the periphery of the screw hole on the side where the fixing bolt is inserted can be automatically formed in an R shape, and can be easily assembled as a guide when the fixing bolt is inserted.

  Moreover, in the compressor of one Embodiment, the said valve holding member consists of steel punching materials.

  According to the compressor of this embodiment, since the valve pressing member is made of a steel punching material, it is possible to reduce the number of steps for changing the burring of the screw hole and to manufacture the valve pressing member at a low cost.

  Moreover, in the compressor of one Embodiment, the said end surface member consists of castings or a sintered material.

  According to the compressor of this embodiment, since the end face member is made of a casting or a sintered material, the end face member can be manufactured at low cost.

  Moreover, in the compressor of one Embodiment, the said discharge valve has a projection part which penetrates into the said discharge hole of the said end surface member.

  According to the compressor of this embodiment, since the discharge valve has a protrusion that enters the discharge hole of the end face member, the protrusion of the discharge valve enters the discharge hole of the end face member. The volume of the discharge hole of the end face member can be further reduced, and the amount of compressed gas remaining in the discharge hole at the end of compression can be further reduced. In this way, a decrease in driving efficiency and an increase in driving sound can be further suppressed.

  Moreover, the sealing part with respect to the said discharge hole of the said discharge valve is securable by the said projection part of the said discharge valve entering the said discharge hole of the said end surface member. Further, when the discharge valve is assembled to the end face member, the discharge valve can be easily assembled to the end face member by positioning the protrusion by inserting the protrusion into the discharge hole.

  In the compressor according to an embodiment, the protrusion of the discharge valve is tapered so that the tip of the protrusion is thin, and the discharge hole of the end surface member has a shape of the protrusion. It is formed in the taper shape corresponding to.

  According to the compressor of this embodiment, since the protrusion and the discharge hole are formed in a tapered shape, the protrusion can be fitted in a state of being substantially aligned with the discharge hole, and the discharge valve The sealing performance with respect to the discharge hole can be further improved.

Further, in the compressor according to one embodiment, the valve pressing member includes a plate-like main body having a hole, and the main body on one side of the main body opposite to the discharge valve with respect to the main body. An annular convex portion provided around the hole portion,
The inner peripheral surface of the hole portion of the main body portion is formed in a cylindrical surface and a tapered surface in order from one surface side of the main body portion to the other surface side, and the inner peripheral surface of the annular convex portion is the same as that of the main body portion. The cylindrical surface has the same diameter as the cylindrical surface and is concentrically connected to the cylindrical surface of the main body, and the cylindrical surface of the main body and the cylindrical surface of the annular protrusion are jointly formed, The screw hole is formed.

  According to the compressor of this embodiment, the inner peripheral surface of the hole portion of the main body portion of the valve pressing member is formed in a cylindrical surface and a tapered surface, so the fixing bolt is connected to the valve pressing member in the valve pressing member. When inserted into the hole, the fixing bolt is aligned by the tapered surface of the hole, and the fixing bolt can be reliably guided to the screw hole.

  Moreover, the part which forms the said taper surface of the said main-body part will have elastic force, and the said screw hole can be diameter-reduced or expanded freely. Therefore, when the fixing bolt is screwed into the screw hole, the initial loosening of the fixing bolt by the screw hole can be prevented.

  Further, since the cylindrical surface of the main body and the cylindrical surface of the annular convex portion jointly form the screw hole, the screw length of the screw hole is determined by the cylindrical surface of the annular convex portion. You can lengthen the length.

  Moreover, in the compressor of one Embodiment, the said screw hole has a screw length larger than the thickness of the said main-body part.

  According to the compressor of this embodiment, the screw hole has a screw length greater than or equal to the thickness of the main body, so that the screw length of the screw hole can be reduced even if the thickness of the main body is reduced. And the fixing bolt can be securely fastened to the screw hole.

Further, in the compressor according to the embodiment, the end surface of the end surface member is provided with a recess portion that accommodates the discharge valve and the valve pressing member, and the recess portion has one side surface and another side surface that are substantially opposed to each other. The one side and the other side are located on both sides of the discharge valve and the valve pressing member so as to substantially position the portions around the fixing bolts of the discharge valve and the valve pressing member,
When the fixing bolt is rotated in the direction of tightening the end face member from the cylinder body side with respect to the screw hole of the valve pressing member, the valve pressing member rotates together with the fixing bolt. In addition, the valve pressing member portion on the discharge hole side with respect to the shaft of the fixing bolt is disposed on the side where the portion abuts,
When the fixing bolt is rotated in the direction of tightening from the cylinder body side of the end face member with respect to the screw hole of the valve pressing member, the valve pressing member rotates together with the fixing bolt. The valve pressing member on the discharge hole side from the shaft of the fixing bolt is disposed on the side away from the shaft.

  According to the compressor of this embodiment, since the recess has the one side surface and the other side surface, when the fixing bolt is tightened against the screw hole, the discharge valve and the valve pressing member are Even if it rotates together with the rotation of the fixing bolt, it is blocked by the one side surface of the recess. Moreover, the said other side surface can guide the said discharge valve and the said valve holding member to the said through-hole side with the said one side surface easily.

  Moreover, in the compressor of one Embodiment, the length from the said through hole in the said one side surface to the said discharge hole side is longer than the length from the said through hole in the said other side surface to the said discharge hole side.

  According to the compressor of this embodiment, the length from the through hole to the discharge hole side on the one side surface is longer than the length from the through hole to the discharge hole side on the other side surface. When the bolt is tightened against the screw hole, the discharge valve and the valve pressing member are reliably blocked by the one side surface of the recess even if the discharge valve and the valve pressing member rotate together following the rotation of the fixing bolt. . Moreover, since the said other side surface is shorter than the said one side surface, the space of the said other side surface of the said hollow part can be enlarged, and reduction of the said discharge space can be prevented. Therefore, the rotational position accuracy when the discharge valve and the valve pressing member are assembled can be improved by the one side surface of the recess, and an increase in discharge pressure loss can be avoided by the other side of the recess.

  Further, in the compressor according to one embodiment, the discharge valve has a lid portion that contacts or separates from the discharge hole, and when the fixing bolt is rotated in a direction to be tightened from the cylinder body side of the end surface member, The discharge valve rotates together with the valve holding member, and when the portion of the discharge valve closer to the discharge hole than the shaft of the fixing bolt comes into contact with the one side surface of the recess portion, the discharge valve The center of the lid portion substantially coincides with the center of the discharge hole.

  According to the compressor of this embodiment, when the discharge valve comes into contact with the one side surface of the recess, the center of the lid portion of the discharge valve and the center of the discharge hole substantially coincide with each other. Therefore, when the fixing bolt is tightened with respect to the screw hole, the discharge valve follows the rotation of the fixing bolt, rotates together with the valve pressing member, and comes into contact with the one side surface of the recess. Therefore, by tightening the fixing bolt, the center of the lid portion of the discharge valve and the center of the discharge hole can be substantially coincided with each other, and the positional accuracy between the discharge valve and the discharge hole is further improved. it can.

  In the compressor according to an embodiment, the concave portion forms a Helmholtz-type resonance chamber, and the cylinder body is provided with a connecting passage that connects the resonance chamber and the cylinder chamber.

  According to the compressor of this embodiment, the recess forms a Helmholtz-type resonance chamber, so that the wavelength of the pulsation sound of the refrigerant gas generated when compressed in the cylinder chamber is from the resonance chamber. It interferes with the interference wave and attenuates greatly. Therefore, the pulsation noise is reduced and noise can be reduced. Therefore, the said recessed part can serve as the space which accommodates a bolt head, and a resonance chamber.

  According to the compressor of the present invention, the fixing bolt is inserted into the through hole of the end surface member and screwed into the screw hole of the valve pressing member, and the discharge valve is connected to the end surface member. Therefore, the thickness of the end face member can be reduced, the volume of the discharge hole of the end face member can be reduced, and a reduction in operating efficiency and an increase in operating sound can be prevented.

  Hereinafter, the present invention will be described in detail with reference to the illustrated embodiments.

(First embodiment)
FIG. 1 is a sectional view showing an embodiment of the compressor of the present invention. The compressor of the present invention is a so-called high-pressure dome type rotary compressor, in which a compressor 2 and a motor 3 are arranged in a casing 1 and an upper part, respectively. The compressor 6 is driven by the rotor 6 of the motor 3 via the drive shaft 12.

  The compression unit 2 sucks wet gas (refrigerant) from the accumulator 10 through the suction pipe 11. The wet gas is obtained by controlling a condenser, an expansion mechanism, and an evaporator (not shown) that constitute an air conditioner as an example of a refrigeration system together with the compressor.

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

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

  The drive shaft 12 passes through the upper end surface member 23 and the lower end surface member 24 and enters the cylinder chamber 22.

  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 right chamber of the blade 28, the suction pipe 11 opens on the inner surface of the cylinder chamber 22 to form a suction chamber 22a. On the other hand, in the chamber on the left side of the blade 28, the discharge hole 23a shown in FIG. 1 opens in the inner peripheral surface of the cylinder chamber 22 to form a discharge chamber 22b.

  Semi-circular bushes 25, 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, 25 with the lubricating oil 9.

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

  As the roller 27 revolves in the cylinder chamber 22, the blade 28 advances and retreats with both side surfaces of the blade 28 being held by the bushes 25, 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 a high-pressure refrigerant is discharged from the discharge hole 23a.

  As shown in FIGS. 1 and 3, the upper end member 23 (hereinafter referred to as end member 23) is provided in the vicinity of the discharge hole 23a communicating with the cylinder chamber 22 and the outside of the discharge hole 23a. Through-holes 23b.

  The end face member 23 is provided with a plate-like discharge valve 31 and a plate-like valve pressing member 32. The discharge valve 31 opens and closes the discharge hole 23 a, and the valve pressing member 32 sandwiches the discharge valve 31 in cooperation with the end surface member 23. The discharge valve 31 has a hole 31a, and the valve pressing member 32 has a screw hole 32a.

  The discharge valve 31 and the valve pressing member 32 are fixed to the end face member 23 by a fixing bolt 33. That is, the head 33 a of the fixing bolt 33 is disposed on the cylinder body 21 side of the end surface member 23, the fixing bolt 33 is inserted into the through hole 23 b of the end surface member 23, and the discharge valve The discharge valve 31 is sandwiched between the end face member 23 and the valve pressing member 32 while being inserted into the hole 31 a of the valve 31 and screwed into the screw hole 32 a of the valve pressing member 32.

  The discharge valve 31 closes the discharge hole 23a in a free state. On the other hand, when the refrigerant (compressed gas) in the cylinder chamber 22 reaches a predetermined pressure, the compressed gas elastically deforms the discharge valve 31 and is discharged from the discharge hole 23a. 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.

  A cup-shaped muffler main body 40 is attached to the end face member 23 so as to cover the discharge valve 31. The muffler main body 40 is fixed to the end face member 23 by a fixing member (such as a bolt).

  A muffler chamber 41 is formed by the muffler main body 40 and the end face member 23. The muffler chamber 41 and the cylinder chamber 22 communicate with each other via 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.

  According to the compressor having the above-described configuration, the fixing bolt 33 is inserted into the through-hole 23b of the end surface member 23 and is screwed into the screw hole 32a of the valve pressing member 32. Since 31 is sandwiched between the end face member 23 and the valve pressing member 32, it is not necessary to cut a screw in the through hole 23b of the end face member 23, and the thickness of the end face member 23 around the through hole 23b. Can be thinned. That is, the axial dimension (thickness direction) of the discharge hole 23a of the end face member 23 can be reduced.

  Thus, the volume of the discharge hole 23a of the end face member 23 (hereinafter referred to as top clearance) 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 the compressed gas from the inside of 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 32a of the valve pressing member 32 are screw-coupled, compared to the case where the valve pressing member 32 and the end surface member 23 are fixed with a rivet, The fixing bolt 33 can be retightened, and the alignment of the discharge valve 31 and the discharge hole 23a can be corrected. For example, the seal check can be easily aligned.

  Furthermore, compared with the case where the said valve holding member 32 and the said end surface member 23 are fixed with a screw and a nut, the number of parts reduces and the working efficiency of an assembly improves.

  The cylinder body 21 has a recess 21 a that accommodates the head portion 33 a of the fixing bolt 33 on the end surface of the cylinder body 21. Thus, the head 33 a of the fixing bolt 33 can be hidden in the recess 21 a on the end surface of the cylinder body 21. Therefore, since the fixing bolt 33 can be disposed avoiding the cylinder chamber 22, the through hole 23 b of the end surface member 23 through which the fixing bolt 33 is inserted is not a bypass passage of the cylinder chamber 22, but is compressed. There is no performance degradation.

  The end face member 23 is made of a casting or a sintered material. In this way, the end face member 23 can be manufactured at low cost. That is, even if the thickness of the portion where the discharge valve 31 is fixed in the end face member 23 is reduced, the end face member 23 is only subjected to compressive stress. Therefore, the end face member 23 is cast or baked as a brittle material. A binder can be used.

(Second Embodiment)
FIG. 4 shows a second embodiment of the present invention. In the second embodiment, the screw hole 42a of the valve pressing member 42 is subjected to burring. The valve pressing member 42 is made of a steel punching material having a spreadability. Note that the same reference numerals as those in the first embodiment have the same configurations as those in the first embodiment, and thus description thereof is omitted.

  Thus, since the screw hole 42a of the valve pressing member 42 is subjected to burring, an effective screw length can be secured without increasing the thickness of the valve pressing member 42. In addition, the periphery of the screw hole 42a on the side where the fixing bolt 33 is inserted can be automatically chamfered in an R shape, and can be easily assembled as a guide when the fixing bolt 33 is inserted. Can do.

  Since the valve pressing member 42 is made of a steel punching material, it is possible to reduce the man-hour for changing the burring of the screw hole 42a, and to manufacture the valve pressing member 42 at a low cost.

(Third embodiment)
FIG. 5 shows a third embodiment of the present invention. In the third embodiment, the end face member 53 has a discharge hole 53a through which compressed gas is discharged and a through hole 53b through which the fixing bolt 33 is inserted. The discharge valve 51 has a hole 51 a through which the fixing bolt 33 is inserted and a protrusion 51 b that enters the discharge hole 53 a of the end surface member 53. Note that the same reference numerals as those in the first embodiment have the same configurations as those in the first embodiment, and thus description thereof is omitted.

  Specifically, the protrusion 51b of the discharge valve 51 is formed in a taper shape so that the tip of the protrusion 51b is thin. The discharge hole 53a of the end face member 53 is formed in a taper shape corresponding to the shape of the protrusion 51b.

  Thus, since the discharge valve 51 has the protrusion 51b that enters the discharge hole 53a of the end face member 53, the protrusion 51b of the discharge valve 51 enters the discharge hole 53a of the end face member 53. Thus, the volume of the discharge hole 53a of the end face member 53 can be further reduced, and the amount of compressed gas remaining in the discharge hole 53a at the end of compression can be further reduced. Therefore, it is possible to further suppress a decrease in driving efficiency and an increase in driving sound.

  Further, since the protrusion 51b of the discharge valve 51 enters the discharge hole 53a of the end face member 53, the sealing performance of the discharge valve 51 with respect to the discharge hole 53a can be secured. Further, when the discharge valve 51 is assembled to the end face member 53, the discharge valve 51 can be easily assembled to the end face member 53 by positioning the projection 51b into the discharge hole 53a.

  Further, since the protrusion 51b and the discharge hole 53a are formed in a taper shape, the protrusion 51b can be fitted in a state substantially coincident with the discharge hole 53a, and the discharge hole of the discharge valve 51 can be fitted. The sealing performance with respect to 53a can be further improved.

  Further, since the axial dimension of the discharge hole 53a is small, the height dimension of the protrusion 51b can be set small. Thus, since the height dimension of the protruding portion 51b can be set small, it is possible to prevent the component accuracy of the protruding portion 51b from being lowered.

(Fourth embodiment)
FIG. 6 shows a fourth embodiment of the present invention. In the fourth embodiment, the valve pressing member 60 includes a plate-shaped main body portion 61 and an annular convex portion 66 provided on one surface of the main body portion 61 opposite to the discharge valve 31 with respect to the main body portion 61. Have Note that the same reference numerals as those in the first embodiment shown in FIG. 3 have the same configurations as those in the first embodiment, and thus the description thereof is omitted.

  The main body 61 has a hole 62. The inner peripheral surface 63 of the hole 62 of the main body 61 is formed in a cylindrical surface 63 a and a tapered surface 63 b in order from one surface side to the other surface side of the main body portion 61. The cylindrical surface 63 a extends in the thickness direction of the main body 61. The tapered surface 63b gradually expands to the other surface side of the main body portion 60. That is, the tapered surface 63b is a chamfered surface.

  The annular protrusion 66 is provided around the hole 62 of the main body 61. An inner peripheral surface 67 of the annular convex portion 66 is formed on a cylindrical surface 67a. The cylindrical surface 67 a has the same diameter as the cylindrical surface 63 a of the main body 61 and is concentrically connected to the cylindrical surface 63 a of the main body 61.

  The cylindrical surface 63a of the main body 61 and the cylindrical surface 67a of the annular convex portion 66 jointly form a screw hole 60a. The screw length of the screw hole 60a can be increased by the cylindrical surface 67a of the annular convex portion 66. That is, the screw hole 60 a has a screw length A that is not less than the thickness t of the main body 61.

  The tapered surface 63b and the annular convex portion 66 are formed by, for example, a punching press. That is, the tapered surface 63b of the main body portion 61, the cylindrical surface 63a of the main body portion 61, and the cylindrical surface 67a of the annular convex portion 66 are formed in order from the punching direction.

  According to the compressor having the above configuration, the inner peripheral surface 63 of the hole 62 of the main body 61 of the valve pressing member 60 is formed on the cylindrical surface 63a and the tapered surface 63b. When the 33 is inserted into the hole 62 of the valve pressing member 60, the fixing bolt 33 is aligned by the tapered surface 63b of the hole 62, and the fixing bolt 33 is securely inserted into the screw hole 60a. Can lead to.

  Moreover, the part which forms the said taper surface 63b of the said main-body part 61 has an elastic force, and the said screw hole 60a can be diameter-reduced or expanded freely. That is, the tapered surface 63b of the main body 61 is an elastic deflection allowance B. Therefore, when the fixing bolt 33 is screwed into the screw hole 60a, the initial loosening of the fixing bolt 33 by the screw hole 60a can be prevented.

  Further, since the screw hole 60a has a screw length A larger than the thickness t of the main body portion 61, the screw length A of the screw hole 60a is reduced even if the thickness t of the main body portion 61 is reduced. And the fixing bolt 33 can be securely fastened to the screw hole 60a.

  Thus, the fixing bolt 33 is less likely to loosen. Therefore, even if the head 33 a of the fixing bolt 33 is on the cylinder body 21 side (shown in FIG. 3), the fixing bolt 33 is placed in the cylinder body 21. I will not fall. Therefore, it is not necessary to disassemble the assembled end face member 23 and the cylinder main body 21 and take out the fixing bolt 33 dropped into the cylinder main body 21, and it is excellent in reliability and durability.

(Fifth embodiment)
7 and 8 show a fifth embodiment of the present invention. In the fifth embodiment, the end face of the end face member 83 is provided with a recess 84 that accommodates the discharge valve 71 and the valve pressing member 32. Note that the same reference numerals as those in the first embodiment shown in FIG. 3 have the same configurations as those in the first embodiment, and thus the description thereof is omitted.

  The recess 84 has a side surface 84a and another side surface 84b that are substantially opposed to each other. The one side surface 84a and the other side surface 84b are located on both sides of the discharge valve 71 and the valve pressing member 32 so as to substantially position the portions around the fixing bolts 33, respectively.

  The one side surface 84a and the other side surface 84b extend from the through hole 83b to the discharge hole 83a side. The discharge hole 83a and the through hole 83b are provided in the end face member 83, and are the same as the discharge hole 23a and the through hole 23b of the end face member 23 shown in FIG.

  When the one side surface 84a is rotated in the direction in which the fixing bolt 33 is tightened from the cylinder body 21 side of the end surface member 83 with respect to the screw hole 32a of the valve pressing member 32, the valve pressing member 32 is It rotates together with the fixing bolt 33 and is arranged on the side where the portion of the valve pressing member 32 on the discharge hole 83a side comes into contact with the shaft of the fixing bolt 33. In addition, in FIG. 8, the direction which fastens the said fixing bolt 33 is shown to the arrow R direction.

  The other side surface 84b is configured such that when the fixing bolt 33 is rotated with respect to the screw hole 32a of the valve pressing member 32 in a direction of tightening from the cylinder body 21 side of the end surface member 83, the valve pressing member 32 is Along with the fixing bolt 33, the valve pressing member 32 on the discharge hole 83 a side is disposed on the side away from the shaft of the fixing bolt 33.

  The length C from the through hole 83b to the discharge hole 83a side in the one side surface 84a is longer than the length D from the through hole 83b to the discharge hole 83a side in the other side surface 84b. Specifically, the length components in the direction connecting the center of the discharge hole 83a and the center of the through hole 83b as compared with the axial direction of the fixing bolt 33 are compared.

  The side surfaces of the discharge valve 71 and the valve pressing member 32 around the fixing bolt 33 are substantially parallel to a line connecting the through hole 83b and the discharge hole 83a. The one side surface 84a and the other side surface 84b are smooth surfaces and are slightly inclined with respect to a line connecting the through hole 83b and the discharge hole 83a.

  The discharge valve 71 has a lid portion 72 that contacts or separates from the discharge hole 83a. When the fixing bolt 33 is rotated in a direction to tighten the end face member 83 from the cylinder body 21 side, the discharge valve 71 rotates together with the valve pressing member 32 due to friction with the valve pressing member 32.

  When the portion of the discharge valve 71 closer to the discharge hole 83a than the shaft of the fixing bolt 33 is in contact with the one side surface 84a of the recess 84, the lid portion 72 of the discharge valve 71 is The center and the center of the discharge hole 83a substantially coincide with each other.

  According to the compressor having the above configuration, the length C from the through hole 83b to the discharge hole 83a side in the one side surface 84a is the length from the through hole 83b to the discharge hole 83a side in the other side surface 84b. Since it is longer than D, when the fixing bolt 33 is tightened against the screw hole 32a, the discharge valve 71 and the valve pressing member 32 may follow the rotation of the fixing bolt 33 and rotate together. The depression 84 is reliably blocked by the one side surface 84a.

  In addition, since the other side surface 84b is shorter than the one side surface 84a, the space on the side of the other side surface 84b of the recess 84 can be increased, and the discharge space can be prevented from being reduced. That is, as shown in FIG. 1, the muffler body 40 is attached to the end face member 83, and the space of the recess 84 can be increased, so that the space of the muffler chamber 41 can be increased. In FIG. 7, the muffler main body 40 is omitted.

  The other side surface 84b can easily guide the discharge valve 71 and the valve pressing member 32 to the through hole 83b side together with the one side surface 84a.

  Therefore, the rotational position accuracy during assembly of the discharge valve 71 and the valve pressing member 32 can be improved by the one side surface 84a side of the recess portion 84, and the discharge pressure loss can be improved by the other side surface 84b side of the recess portion 84. Can be avoided.

  Further, when the discharge valve 71 comes into contact with the one side surface 84a of the hollow portion 84, the center of the lid portion 72 of the discharge valve 71 and the center of the discharge hole 83a substantially coincide with each other. When the fixing bolt 33 is tightened with respect to the screw hole 32 a, the discharge valve 71 follows the rotation of the fixing bolt 33 and rotates together with the valve pressing member 32, and the one side surface of the recess 84. 84a abuts. Therefore, by tightening the fixing bolt 33, the center of the lid portion 72 of the discharge valve 71 and the center of the discharge hole 83a can be substantially coincided with each other, and the discharge valve 71 and the discharge hole 83a The position accuracy can be further improved.

  In short, the one side surface 84 a has a function of positioning the discharge valve 31. The one side surface 84 a and the other side surface 84 b have a function of guiding the discharge valve 71 and the valve pressing member 32.

  The one side surface 84a may not have a smooth surface but may have a convex portion. When the discharge valve 71 comes into contact with the convex portion of the one side surface 84a, the lid of the discharge valve 71 is provided. What is necessary is just to make it the center of the part 72 and the center of the said discharge hole 83a correspond substantially. Further, the length C of the one side surface 84a may not be longer than the length D of the other side surface 84b. When the fixing bolt 33 is tightened, the discharge valve 71 and the valve pressing member 32 are Even if it rotates together with the rotation of the fixing bolt 33, it is blocked by the one side surface 84 a of the recess 84.

(Sixth embodiment)
FIG. 9 shows a sixth embodiment of the present invention. In the sixth embodiment, the end face of the cylinder main body 121 has a recess 121 a for accommodating the head 33 a of the fixing bolt 33, and the recess 121 a forms a Helmholtz-type resonance chamber 130. Note that the same reference numerals as those in the first embodiment shown in FIG. 3 have the same configurations as those in the first embodiment, and thus the description thereof is omitted.

  The resonance chamber 130 is a space defined by the recess 121 a and the end surface member 23. The cylinder body 121 is provided with a connecting passage 121 b that connects the resonance chamber 130 and the cylinder chamber 122.

  The connection passage 121 b is a groove provided on the end surface of the cylinder body 121. The connection passage 121b opens in the vicinity of the discharge hole 23a. The connecting passage 121b may be formed by a hole penetrating the cylinder body 121.

  According to the compressor configured as described above, the concave portion 121a forms the Helmholtz-type resonance chamber 130. Therefore, the wavelength of the pulsation sound of the refrigerant gas generated when the cylinder chamber 122 is compressed is the resonance chamber. It interferes with the interference wave from 130 and is greatly attenuated. Therefore, the pulsation noise is reduced and noise can be reduced. Therefore, the recess 121a can serve as a space for accommodating the bolt head 33a and a resonance chamber.

  In addition, this invention is not limited to the above-mentioned embodiment. For example, in the above-described embodiment, a swing compressor in which the roller 27 and the blade 28 are integrated, but a compressor in which the roller and the blade are separated may be used. A reciprocating compressor may also be used. The discharge valve 31 may not be provided with the hole 31a through which the fixing bolt 33 is inserted, and the discharge valve 31 may be held between the end face member 23 and the valve pressing member 32. The discharge valves 31, 51, 71, the valve pressing members 32, 42, 60 and the fixing bolt 33 may be attached to the lower end surface member 24. The recess 21 a is not limited to a space having a bottom surface, and may be a hole that penetrates the cylinder body 21.

It is sectional drawing which shows 1st Embodiment of the compressor of this invention. It is a top view of a compressor. It is a principal part expanded sectional view which shows 1st Embodiment of the compressor of this invention. It is a principal part expanded sectional view which shows 2nd Embodiment of the compressor of this invention. It is a principal part expanded sectional view which shows 3rd Embodiment of the compressor of this invention. It is a principal part expanded sectional view which shows 4th Embodiment of the compressor of this invention. It is a top view which shows 5th Embodiment of the compressor of this invention. It is a principal part expanded sectional view of FIG. It is a principal part expanded sectional view which shows 6th Embodiment of the compressor of this invention. It is a principal part expanded sectional view of the conventional compressor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Casing 2 Compression part 3 Motor 12 Drive shaft 21, 121 Cylinder main body 21a, 121a Recess 22, 122 Cylinder chamber 22a Suction chamber 22b Discharge chamber 23, 53, 83 (Upper) end surface member 23a, 53a, 83a Discharge hole 23b, 53b, 83b Through hole 25 Bush 26 Crank pin 27 Roller 28 Blade 31, 51, 71 Discharge valve 31a, 51a, 71a Hole 51b Projection 32, 42, 60 Valve pressing member 32a, 42a, 60a Screw hole 33 Fixing bolt 33a Head portion 61 Body portion 62 Hole portion 63 Inner peripheral surface 63a Cylindrical surface 63b Tapered surface 66 Annular convex portion 67 Inner peripheral surface 67a Cylindrical surface 72 Lid portion 84 Depressed portion 84a One side surface 84b Other side surface 121b Connection passage 130 Helmholtz type resonance chamber A (Screw hole) Screw length C (One side ) Length D (other side) length t (the main body) Thickness

Claims (13)

A cylinder body (21, 121) forming a cylinder chamber (22, 122);
End face members (23a, 53a, 83a) that are attached to the end faces of the cylinder bodies (21, 121) and communicate with the cylinder chambers (22, 122) and through holes (23b, 53b, 83b) ( 23, 53, 83)
Discharge valves (31, 51, 71) for opening and closing the discharge holes (23a, 53a, 83a) of the end face members (23, 53, 83);
A valve presser member (32, 42, 60) having a screw hole (32a, 42a, 60a) and interposing the discharge valve (31, 51, 71) in cooperation with the end face member (23, 53, 83); ,
A fixing bolt (33) having a head (33a),
The head (33a) of the fixing bolt (33) is disposed on the cylinder body (21, 121) side of the end face member (23, 53, 83), and the fixing bolt (33) is the end face member. (23, 53, 83) is inserted into the through hole (23b, 53b, 83b) and screwed into the screw hole (32a, 42a, 60a) of the valve pressing member (32, 42, 60). In the state, the discharge valve (31, 51, 71) is sandwiched between the end face member (23, 53, 83) and the valve pressing member (32, 42, 60). The compressor according to claim 1,
The cylinder body (21, 121) has a recess (21a, 121a) for accommodating the head (33a) of the fixing bolt (33) on an end surface of the cylinder body (21, 121). Compressor. The compressor according to claim 1,
The compressor, wherein the screw hole (42a) of the valve pressing member (42) is subjected to burring. The compressor according to claim 3, wherein
The compressor, wherein the valve pressing member (42) is made of a steel punched material. The compressor according to claim 1,
The compressor according to claim 1, wherein the end face members (23, 53, 83) are made of a casting or a sintered material. The compressor according to claim 1,
The compressor, wherein the discharge valve (51) has a protrusion (51b) that enters the discharge hole (53a) of the end face member (53). The compressor according to claim 6, wherein
The protrusion (51b) of the discharge valve (51) is formed in a taper shape so that the tip of the protrusion (51b) becomes thin,
The compressor, wherein the discharge hole (53a) of the end surface member (53) is formed in a taper shape corresponding to the shape of the protrusion (51b). The compressor according to claim 1,
The valve pressing member (60)
A plate-like main body (61) having a hole (62);
The main body (61) is provided on one surface of the main body (61) opposite to the discharge valve (31, 51, 71) around the hole (62) of the main body (61). An annular projection (66),
The inner peripheral surface (63) of the hole (62) of the main body (61) is formed into a cylindrical surface (63a) and a tapered surface (63b) in order from one surface side to the other surface side of the main body portion (61). Formed,
An inner peripheral surface (67) of the annular convex portion (66) has the same diameter as the cylindrical surface (63a) of the main body portion (61) and is concentric with the cylindrical surface (63a) of the main body portion (61). Formed in a cylindrical surface (67a) that is continuous in a shape,
The cylindrical surface (63a) of the main body (61) and the cylindrical surface (67a) of the annular protrusion (66) jointly form the screw hole (60a). Compressor. The compressor according to claim 8, wherein
The compressor is characterized in that the screw hole (60a) has a screw length (A) larger than the thickness (t) of the main body (61). The compressor according to claim 1,
The end surface of the end surface member (83) is provided with a recess (84) that houses the discharge valve (71) and the valve pressing member (32, 42, 60),
The hollow portion (84) has one side surface (84a) and the other side surface (84b) that are substantially opposed to each other,
The one side surface (84a) and the other side surface (84b) are positioned so as to substantially position portions around the fixing bolt (33) of the discharge valve (71) and the valve pressing member (32, 42, 60). Located on both sides of this site,
The one side surface (84a) is formed by fixing the fixing bolt (33) to the cylinder body of the end surface member (83) with respect to the screw hole (32a, 42a, 60a) of the valve pressing member (32, 42, 60). When rotated in the tightening direction from the (21, 121) side, the valve pressing member (32, 42, 60) rotates together with the fixing bolt (33), and more than the shaft of the fixing bolt (33). While the portion of the valve pressing member (32, 42, 60) on the discharge hole (83a) side is disposed on the side where it abuts,
The other side surface (84b) is formed by fixing the fixing bolt (33) to the cylinder body of the end surface member (83) with respect to the screw hole (32a, 42a, 60a) of the valve pressing member (32, 42, 60). When rotated in the tightening direction from the (21, 121) side, the valve pressing member (32, 42, 60) rotates together with the fixing bolt (33), and more than the shaft of the fixing bolt (33). A compressor characterized in that a portion of the valve pressing member (32, 42, 60) on the discharge hole (83a) side is disposed on a side to be separated. The compressor according to claim 10, wherein
The length (C) from the through hole (83b) to the discharge hole (83a) side in the one side surface (84a) is the length from the through hole (83b) in the other side surface (84b) to the discharge hole (83a). The compressor characterized by being longer than the length (D) to the side. The compressor according to claim 10, wherein
The discharge valve (71) has a lid (72) that contacts or separates from the discharge hole (83a),
When the fixing bolt (33) is rotated in the direction of tightening from the cylinder body (21, 121) side of the end face member (83), the discharge valve (71) is connected to the valve pressing member (32, 42, 60). )
When the portion of the discharge valve (71) closer to the discharge hole (83a) than the shaft of the fixing bolt (33) contacts the one side surface (84a) of the recess (84), the discharge The compressor characterized in that the center of the lid (72) of the valve (71) and the center of the discharge hole (83a) substantially coincide. The compressor according to claim 2, wherein
The recess (121a) forms a Helmholtz-type resonance chamber (130),
The compressor characterized in that the cylinder body (121) is provided with a connecting passage (121b) for connecting the resonance chamber (130) and the cylinder chamber (122).

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