JP2015209822A - Vibration type compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To fix a suction valve to a piston in such a way that a dead space is scarcely left in the piston under a compression stroke of the piston and a volumetric efficiency may be improved.SOLUTION: A suction valve 25 is constituted by a valve seat member 30 fixed to a head part of a piston 17 adjacent to a pump chamber 23 and having a valve hole 34 opened at a suction port 24 at its center; and a valve plate 31 made from a thin steel plate fixed to the valve seat member 30 so as to form a substantial one planar plane together with an end surface of the head part. The valve plate 31 is constituted by an annular supporting part 31a fixed to an outer circumferential part of the valve seat member 30, a valve part 31b for opening or closing the valve hole 34, a plurality of resilient arms 31c forming a concentric arcuate shape with the valve part 31b to connect between the supporting part 31a and the valve part 31b, and slits 31d arranged at both sides of these resilient arms 31c to cause between the valve hole 34 and the pump chamber 23 to be communicated when the valve part 31b is opened.

Description

  The present invention relates to a vibration type compressor mainly applied to a refrigerator mounted on an automobile, and in particular, a cylinder block and a pump chamber that is reciprocally fitted in a cylinder hole of the cylinder block to define a pump chamber. A piston, a vibration source for reciprocating the piston, a discharge chamber adjacent to the pump chamber, a suction port provided in the piston, and between the suction port and the pump chamber according to the reciprocation of the piston. A suction valve that opens and closes to generate a gas flow in one direction from the suction port to the pump chamber, and opens and closes the pump chamber and the discharge chamber in accordance with the reciprocating movement of the piston. The present invention relates to an improvement of a vibration type compressor including a discharge valve that generates a gas flow in one direction.

  Such a vibration type compressor is known as disclosed in Patent Document 1 below.

JP 2011-94568 A

  As shown in FIG. 11, in the conventional vibration type compressor, the piston 17 is composed of a piston body 17a having a small-diameter portion 17a1 at the tip and a piston head 17b that is press-fitted into the small-diameter portion 17a1 and faces the pump chamber 23. In addition, an annular valve chamber 16 is defined between the inward flange portion 17b1 of the piston head 17b and the small diameter portion 17a1, and the valve chamber 16 is formed on the end surface of the small diameter portion 17a1 of the piston body 17a. The valve plate 9 that opens and closes the intake port 24 of the piston 17 in cooperation with the valve seat 8 is accommodated to constitute the intake valve 25, and the valve plate 9 is separated from the valve seat 8 during the intake stroke of the piston 17. As a result, gas is sucked from the suction port 24 of the piston 17 into the pump chamber 23 through the notch 9a on the outer periphery of the valve plate 9, and is pumped by the valve closing seating of the valve plate 9 to the valve seat 8 during the compression stroke of the piston 17. 23 gas is compressed, and is pumped to the discharge chamber through the discharge valve (not shown).

  By the way, in the compression stroke of the piston 17, the inner space a of the inward flange portion 17b1 of the piston head 17b and the open / close movable space b of the valve plate 9 in the valve chamber 16 become dead spaces, which hinder the improvement of the volume efficiency. This is one factor that reduces the maximum gas discharge rate. Further, when the valve plate 9 is opened and closed, the whole of the valve plate 9 vibrates in the axial direction, thereby generating noise due to the collision with the flange portion 17b1 and the seating with the valve seat 8, that is, the valve body 9 is reciprocated once. Two collision sounds will be generated.

  The present invention has been made in view of such circumstances, and the suction valve can be attached to the piston so that there is almost no dead space in the piston in the compression stroke of the piston, and the volumetric efficiency is improved. It is an object of the present invention to provide the vibration type compressor having a low operating noise of the suction valve.

  In order to achieve the above object, the present invention provides a cylinder block, a piston that is reciprocally fitted in a cylinder hole of the cylinder block to define a pump chamber in the cylinder hole, and a reciprocating motion to the piston. The vibration source to be applied, the discharge chamber adjacent to the pump chamber, the suction port provided in the piston, and the suction port and the pump chamber are opened and closed according to the reciprocation of the piston, and the suction port is connected to the pump chamber. Opening and closing the pump chamber and the discharge chamber according to the reciprocating movement of the piston and the suction valve that generates a gas flow in one direction, and generates a gas flow in one direction from the pump chamber to the discharge chamber. In a vibration type compressor including a discharge valve, a valve seat member fixed to a head portion of a piston facing the pump chamber and having a valve hole that opens to the suction port in a central portion, and an end surface of the head portion The suction valve is constituted by a thin steel plate valve plate fixed to the valve seat member so as to form a flat surface, and the annular support portion is fixed to the outer peripheral portion of the valve seat member. And a valve portion for opening and closing the valve hole, a plurality of elastic arm portions concentric with the valve portion to connect the support portion and the valve portion, and provided on both sides of the elastic arm portions, A first feature is that the valve portion is configured by a slit that conducts between the valve hole and the pump chamber when the valve portion is opened. The vibration source corresponds to the drive coil 19 in an embodiment of the present invention described later, and the discharge valve corresponds to the second discharge valve 39.

  According to the present invention, in addition to the first feature, the valve seat member is housed in a recess formed in the head end surface of the piston, and the valve seat member has an annular protrusion protruding from the inner peripheral surface of the piston. A second feature is that a caulking portion penetrating the inner peripheral side is formed, the caulking portion is caulked radially outward, and the annular protrusion is sandwiched between the caulking portion and the valve seat member.

  Furthermore, in addition to the first or second feature, the present invention extends a fixing portion that protrudes in the radial direction from the outer periphery of the support portion, and embraces the outer peripheral portion of the valve seat member by the fixing portion. The third feature is that the support portion is fixed to the valve seat member.

  According to the first aspect of the present invention, in the intake valve attached to the piston head, the valve plate is fixed to the valve seat member so as to form a substantially flat surface together with the end surface of the piston head. In the piston head, there is almost no dead space, and the volumetric efficiency of the pump chamber can be effectively increased during the compression stroke of the piston, so that the pump efficiency can be improved. The valve plate includes an annular support portion fixed to the outer periphery of the valve seat member, a valve portion for opening and closing the valve hole of the valve seat member, and an arc shape concentric with the valve portion. The valve portion is composed of a plurality of elastic arm portions that connect the portions, and slits that are provided on both sides of the elastic arm portions and that conduct between the valve hole and the pump chamber when the valve portion is opened. Since the inertia weight is small, the seating sound on the valve seat member is extremely small, and the quietness of the suction valve can be obtained. In addition, when the valve part is opened, the gas that has passed through the valve hole spreads radially by hitting the valve part and then moving to the pump chamber from an arc that is concentric with the valve part. The lubricating oil contained in the cylinder can collide with, adhere to and separate from the inner peripheral surface of the cylinder hole, and the lubricating oil can lubricate the sliding portion with the piston on the inner surface of the cylinder hole.

  According to the second feature of the present invention, the valve seat member is fixed to the piston by sandwiching the annular protrusion protruding from the inner peripheral surface of the piston between the caulking portion and the valve seat member. The mounting portion can be prevented from protruding to the pump chamber side, which can contribute to the improvement of the volume efficiency of the pump chamber.

  According to the third feature of the present invention, the support portion is fixed to the valve seat member by embedding the outer periphery portion of the valve seat member by the fixing portion protruding in the radial direction from the outer periphery of the support portion of the valve plate. The valve plate mounting portion is prevented from projecting to the pump chamber side, which can also contribute to the improvement of the volume efficiency of the pump chamber.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a longitudinal side view of a vibration type compressor according to a first embodiment of the present invention. FIG. 2 is an enlarged view of part 2 of FIG. 1. FIG. 3 is an enlarged view taken along arrow 3 in FIG. 2. FIG. FIG. 5 is a sectional view taken along line 5-5 of FIG. FIG. 4 is a view corresponding to FIG. 3 showing a first modification of the valve plate of the intake valve. FIG. 4 is a view corresponding to FIG. 3 showing a second modification of the valve plate of the intake valve. The vertical side view of the vibration type compressor which concerns on 2nd Embodiment of this invention. 9 is an enlarged view of 9 parts in FIG. FIG. 10 is a sectional view taken along line 10-10 in FIG. 8; Sectional drawing around the suction valve in the conventional vibration type compressor.

  Embodiments of the present invention will be described below with reference to the accompanying drawings.

  First, the description starts with the description of the first embodiment of the present invention shown in FIGS. In FIG. 1, the vibration type compressor C of the present invention is installed at an appropriate position of a box as a compressor of a refrigerator mounted on a vehicle such as a truck or a bus. The vibration type compressor C includes a cylindrical container 1 and a compressor main body 2 accommodated in the cylindrical container 1, and an installation bracket 3 is fixed to the lower part of the cylindrical container 1.

  The compressor body 2 includes a cylindrical yoke 4, a core pole 5 that is coupled to one end of the yoke 4 so as to close the yoke 4, and is disposed concentrically inside the yoke 4, and is connected to the other end of the yoke 4. And an end plate 6 coupled so as to close the core pole 5, and a permanent magnet 7 is attached to the outer periphery of the core pole 5.

  A cylinder block 10 is disposed at the center of the core pole 5. The cylinder block 10 protrudes from the outer periphery of the first mounting flange 11, and the cylinder block 10 is fixed to the core pole 5 by fixing the first mounting flange 11 to the end face of the core pole 5. A second mounting flange 13 of the cylinder head 12 aligned coaxially with the cylinder block 10 is joined to the outer end surface of the first mounting flange 11 via a gasket 14.

  A hollow cylindrical piston 17 is slidably fitted into the cylinder hole 15 of the cylinder block 10. The piston 17 has an outer end opposite to the cylinder head 12 protruding from the cylinder hole 15, and a drive coil 19 is connected to the outer end via a coil support 18.

  The coil support 18 includes a cylindrical bobbin 18a disposed between the yoke 4 and the permanent magnet 7, an end wall 18b connected to one end of the bobbin 18a, and a support plate 18c insert-coupled to the end wall 18b. The support plate 18c is fixed to the outer end portion of the piston 17 by press fitting, welding, or the like, and a drive coil 19 is wound around the outer periphery of the bobbin 18a. The bobbin 18a reciprocates between the yoke 4 and the permanent magnet 7 in the axial direction. The end wall 18b is provided with a plurality of through holes 20 that communicate between the inside and the outside.

  A pair of left and right resonance springs 21 are interposed between the end wall 18b, the end plate 6 and the cylinder block 10, and these resonance springs 21 are coil springs, and a predetermined set load is applied in the compression direction. Is granted. Thus, the drive coil 19 is integrally connected to the piston 17 and supported by a pair of resonance springs 21.

  A pump chamber 23 is defined in the cylinder hole 15 by a piston 17. The hollow portion of the piston 17 serves as a suction port 24 that opens into the yoke 4, and a suction valve 25 is disposed between the suction port 24 and the pump chamber 23. The cylinder head 12 is provided with a discharge chamber 26 adjacent to the pump chamber 23, and a discharge valve device 27 is disposed between the pump chamber 23 and the discharge chamber 26.

  As shown in FIGS. 2 and 3, the intake valve 25 includes a valve seat member 30 and an elastic valve plate 31. An annular protrusion 32 is formed on the inner peripheral surface of the piston 17 on the head side facing the pump chamber 23 of the piston 17. Further, a recess 33 having an annular protrusion 32 as a bottom surface is formed on the end surface of the head of the piston 17, and the valve seat member 30 is accommodated in the recess 33. The valve seat member 30 is provided with a valve hole 34 at the center thereof and a cylindrical caulking portion 35 penetrating the inner peripheral side of the annular protrusion 32, and the caulking portion 35 is radially outward. By caulking, the valve seat member 30 is fixed to the annular protrusion 32 by sandwiching the annular protrusion 32 between the caulking portion 35 and the valve seat member 30.

  The elastic valve plate 31 is made of a thin steel plate, and includes an annular support portion 31a fixed to the outer peripheral portion of the valve seat member 30, a valve portion 31b for opening and closing the valve hole 34, and a circle concentric with the valve portion 31b. A plurality of (two in the illustrated example) elastic arm portions 31c that connect the support portion 31a and the valve portion 31b in an arc shape, and are provided on both sides of these elastic arm portions 31c. When the valve portion 31b is opened, The slit 34d is formed between the hole 34 and the pump chamber 23. A plurality of radially extending fixed pieces 36 are extended on the support portion 31 a, and the support portion 31 a is fixed to the valve seat member 30 by embedding the outer peripheral portion of the valve seat member 30 with these fixed pieces 36.

  As shown in FIGS. 2 and 5, the discharge valve device 27 includes first and second discharge valves 38 and 39. The first discharge valve 38 is contracted by the valve seat 40 formed on the end surface of the cylinder block 10 so as to surround the pump chamber 23, a rigid valve plate 41 that can be seated on the valve seat 40, and the discharge chamber 26. It comprises a closing spring 42 that biases the rigid valve plate 41 in the seating direction with the valve seat 40.

  The second discharge valve 39 is provided in the center of the rigid valve plate 41 and communicates between the pump chamber 23 and the discharge chamber 26 and a thin valve that opens and closes the valve hole 45 on the outer end surface side of the rigid valve plate 41. The elastic valve plate 46 is made of a steel plate, and the elastic valve plate 46 is made of a thin steel plate. The annular support portion 46a is pressed and fixed to the outer peripheral portion of the rigid valve plate 41 by the biasing force of the closing spring 42. And a valve part 46b for opening and closing the valve hole 45 on the outer end face side of the rigid valve plate 41, and a plurality of pipes connecting the support part 46a and the valve part 46b in a circular arc concentric with the valve part 46b (see FIG. In the example shown, there are two elastic arm portions 46c, and slits 46d that are provided on both sides of these elastic arm portions 46c and connect between the valve hole 45 and the discharge chamber 26 when the valve portion 46b is opened. Thus, the valve opening pressure of the elastic valve plate 46 is set lower than the valve opening pressure of the rigid valve plate 41.

  Referring again to FIG. 1, a low-pressure pipe 48 connected to the outlet side of the evaporator of the refrigerator and a high-pressure pipe 49 connected to the inlet of the condenser of the refrigerator are attached to one end wall of the cylindrical container 1. The inner end of the low-pressure pipe 48 opens into the cylindrical container 1, and the refrigerant gas that has passed through the low-pressure pipe 48 is released into the cylindrical container 1 and fixed to the first and second mounting flanges 11 and 13. And then into the coil support 18 through a cylindrical passage 51 between the cylinder block 10 and the core pole 5, and through the through hole 20 of the end wall 18 b and the inside of the compressor body 2, the piston 17. To the intake port 24.

  On the other hand, the high-pressure tube 49 includes a first end 49a fixed to the cylindrical container 1, a second end 49b fixed to the second mounting flange 13, and the first and second ends 49a and 49b. The second end portion 49b communicates with the discharge chamber 26 via the communication passage 52 between the first and second mounting flanges 11 and 13. To do.

  Next, the operation of this embodiment will be described.

  When an alternating current is passed through the drive coil 19, the piston 17 reciprocates left and right together with the drive coil 19 according to the polarity of the alternating current, and the reciprocating motion of the piston 17 is amplified by the left and right resonance springs 21. The reciprocating movement of the piston 17 thus amplified, that is, the suction stroke (right movement stroke in FIG. 1) and the discharge stroke (left movement stroke in FIG. 1) are repeated. In the suction stroke, the suction valve 25 is drawn by the suction action of the pump chamber 23. Is opened, the refrigerant gas reaching the suction port 24 from the low pressure pipe 48 is sucked into the pump chamber 23, and in the next discharge stroke, the elastic valve plate 46 is opened by the discharge action of the pump chamber 23, and the pump The refrigerant gas in the chamber 23 is discharged into the discharge chamber 26 and is pumped to the high pressure pipe 49.

  By the way, the intake valve 25 is fixed to the valve seat member 30 so as to form a substantially flat surface together with the valve seat member 30 received and fixed in the recess 33 on the head end surface of the piston 17 and the head end surface of the piston 17. Therefore, there is almost no dead space in the head of the piston 17, and the volumetric efficiency of the pump chamber 23 can be effectively increased during the compression stroke of the piston 17, so that the pump efficiency is improved. Can be improved.

  Further, the elastic valve plate 31 of the intake valve 25 includes an annular support portion 31a fixed to the outer peripheral portion of the valve seat member 30, a valve portion 31b for opening and closing the valve hole 34 of the valve seat member 30, and the valve portion 31b. And a plurality of elastic arm portions 31c connecting the support portion 31a and the valve portion 31b in a concentric arc shape, and provided on both sides of the elastic arm portions 31c. When the valve portion 31b is opened, the valve hole 34 is provided. Since the valve portion 31b has a small inertia weight, the seating noise on the valve seat member 30 is extremely small and the quietness of the intake valve 25 is ensured. Can do. Moreover, when the valve portion 31b is opened, as shown in FIG. 4, the refrigerant gas that has passed through the valve hole 34 strikes the valve portion 31b, and then enters the pump chamber 23 from a slit 31d that is concentric with the valve portion 31b. By shifting, the oil spreads radially, so that the lubricating oil contained in the refrigerant gas can collide with and adhere to the inner peripheral surface of the cylinder hole 15, and the piston 17 on the inner surface of the cylinder hole 15 can be separated by the lubricating oil. The sliding part can be lubricated.

  Further, the valve seat member 30 is formed with a cylindrical caulking portion 35 penetrating the inner peripheral side of the annular protrusion 32 protruding from the inner peripheral surface of the piston 17, and the caulking portion 35 is caulked outward in the radial direction. By clamping the annular protrusion 32 between the caulking portion 35 and the valve seat member 30, the valve seat member 30 is fixed to the piston 17, so that the attachment portion of the valve seat member 30 protrudes toward the pump chamber 23. This can contribute to the improvement of the volumetric efficiency of the pump chamber 23.

  Further, in the elastic valve plate 31, a plurality of fixing pieces 36 projecting in the radial direction from the outer periphery of the support portion 31a are extended, and by holding the outer peripheral portion of the valve seat member 30 by these fixing pieces 36, the support portion Since 31 a is fixed to the valve seat member 30, the attachment portion of the elastic valve plate 31 is prevented from protruding toward the pump chamber 23, which can also contribute to the improvement of the volume efficiency of the pump chamber 23.

  On the other hand, the discharge valve device 27 includes first and second discharge valves 38 and 39, and the valve opening pressure of the elastic valve plate 46 of the second discharge valve 39 is set to open the rigid valve plate 41 of the first discharge valve 38. Since the pressure is set lower than the pressure, the refrigerant gas can be sent from the pump chamber 23 to the discharge chamber 26 by opening and closing the elastic valve plate 46 during the normal reciprocating stroke of the piston 17. In addition, the elastic valve plate 46 is a valve that opens and closes the valve hole 45 on the outer end surface side of the rigid valve plate 41 and an annular support portion 46 a that is pressed and fixed to the outer peripheral portion of the rigid valve plate 41 by the biasing force of the spring 42. Part 46b, a plurality of elastic arm parts 46c concentric with the valve part 46b and connecting the support part 46a and the valve part 46b, and provided on both sides of the elastic arm part 46c. Since the valve portion 46b has a small inertia weight, the seating sound on the rigid valve plate 41 is extremely small, and the discharge valve device 27 has a small inertia weight. The quietness of the can be ensured.

  The first discharge valve 38 is contracted in the discharge chamber 26, a valve seat 40 formed on the end face of the cylinder block 10 so as to surround the pump chamber 23, a rigid valve plate 41 that can be seated on the valve seat 40, and the discharge chamber 26. Since the rigid valve plate 41 is composed of a closing spring 42 that urges the rigid valve plate 41 in the seating direction with respect to the valve seat 40, the rigid valve plate 41 is closed by the piston 17 when the piston 17 overstrokes during the compression stroke. The piston 17 is pushed open against the biasing force of the spring 42, and the overstroke of the piston 17 is allowed. At this time, since the elastic valve plate 46 is held in close contact with the rigid valve plate 41 by the biasing force of the closing spring 42, it is not damaged.

  Further, since the closing spring 42 of the first discharge valve 38 is used for fixing the support portion 31a of the elastic valve plate 31 to the rigid valve plate 41, the structure for fixing the support portion 31a of the elastic valve plate 31 can be simplified. Can do.

  6 and 7 show first and second modified examples of the elastic valve plate 31 of the intake valve 25. In the first modified example of FIG. 6, an elastic arm connecting the support portion 31a and the valve portion 31b. The three portions 31c are arranged at regular intervals around the valve portion 31b. In the second modification of FIG. 7, the elastic arm portions 31c are arranged at four intervals around the valve portion 31b. . Such a modification of the elastic valve plate 31 can also be applied to the elastic valve plate 46 of the second discharge valve 39.

  Next, a second embodiment of the present invention shown in FIGS. 8 to 10 will be described.

  The cylindrical container 1 of the vibration type compressor C includes a barrel 1a and a pair of left and right caps 1b coupled to both ends thereof. The barrel 1a includes a partition wall 55 that bisects the inside, and the partition wall. A pair of left and right cylindrical core poles 56 projecting from both end faces of 55 are integrally formed. A pair of left and right cylinder blocks 10 arranged coaxially are fixed to the inner periphery of these core poles 56 by bolts 57, respectively. A pair of left and right permanent magnets 7 are fixed to the outer peripheral surfaces of the pair of core poles 56 via yokes 58.

  A pair of left and right pistons 17 whose heads are opposed to each other are fitted in the cylinder holes 15 of the pair of cylinder blocks 10, and a pair of drive coils 19 surrounding the pair of permanent magnets 7 at the rear ends of the pistons 17. Are connected to each other. The pair of coil supports 59 are supported by the cylindrical container 1 via the resonance spring 60. As shown in FIG. 10, the resonance spring 60 is composed of a plurality of leaf springs having a band shape with a curved middle portion, and the outer peripheral end portion is sandwiched between the barrel 1a and the cap 1b.

  A suction valve 25 having the same configuration as that of the previous embodiment is attached to the head of each piston 17. A discharge valve device 27 is attached to the front end of each cylinder block 10, and the discharge chamber 26 is provided in common in the core pole 56 so as to surround the left and right cylinder blocks 10.

  The discharge valve device 27 includes first and second discharge valves 38 and 39 as in the previous embodiment, but the first discharge valve 38 differs from the previous embodiment as follows. That is, as clearly shown in FIG. 9, a guide member 61 is slidably fitted on the outer periphery of the front end of each cylinder block 10, and the guide member 61 is rigid in cooperation with the valve seat 40 of the cylinder block 10. An inward flange 61a that can sandwich the valve plate 41 and the elastic valve plate 46 is provided. The left and right guide members 61 are urged toward the valve seat 40 together with the corresponding rigid valve plate 41 and elastic valve plate 46 by a common closing spring 42 urging force.

  The partition wall 55 of the barrel 1a is provided with a common low-pressure passage 62 connected to the outlet of the evaporator. The refrigerant gas passing through the low-pressure passage 62 is divided into the left and right sides of the partition wall 55, and the suction ports 24 inside the left and right pistons 17 are provided. To come to reach.

  The partition wall 55 is provided with a common high-pressure passage 63 that opens to the discharge chamber 26 and communicates with the condenser inlet.

  In FIG. 8 to FIG. 10, the same reference numerals are assigned to the portions corresponding to those of the first embodiment, and the overlapping description is omitted.

  Thus, when an alternating current of opposite phase is supplied to the left and right drive coils 19, the left and right pistons 17 reciprocate in opposite directions together with the corresponding drive coils 19, and the reciprocation of each piston 17 corresponds to the corresponding resonance. Amplified by the spring 60. At that time, since the left and right pistons 17 move in opposite directions, the inertial forces of the left and right pistons 17 cancel each other, and the vibration of the vibration type compressor C can be effectively reduced.

  In the suction stroke of each piston 17, the suction valve 25 is opened by the suction action of the pump chamber 23 as in the previous embodiment, and the refrigerant gas that has reached the suction port 24 from the low-pressure passage 62 enters the pump chamber 23. In the next discharge stroke, the second discharge valve 39 of the discharge valve device 27 is opened by the discharge action of the pump chamber 23, the refrigerant gas in the pump chamber 23 is discharged to the discharge chamber 26, and the high-pressure passage 63. Pumped to

  When each piston 17 overstrokes during the compression stroke and pushes up the rigid valve plate 41, the guide member 61 slides with respect to the cylinder block 10, so that the rigid valve plate 41 supported by the guide member 61 and The posture of the elastic valve plate 46 can be stabilized.

  Although the embodiments of the present invention have been described above, the present invention is not limited thereto, and various design changes can be made without departing from the scope of the present invention. For example, a plurality of fixed pieces 36 of the elastic valve plate 31 of the intake valve 25 are used as an annular fixed wall which is continuous in a circumferential shape, and this is caulked on the back side of the valve seat member 30 over the entire periphery, thereby supporting the support portion 31a. It can also be fixed to.

C: Vibration compressor 10 ... Cylinder block 15 ... Cylinder hole 17 ... Piston 19 ... Vibration source (drive coil)
23 ... Pump chamber 24 ... Suction port 25 ... Suction valve 26 ... Discharge chamber 30 ... Valve seat member 31 ... Elastic valve plate 31a ... Support 31b ... Valve part 31c ... Elastic arm part 31d ... Slit 32 ... Ring projection 33 ... Recess 34 ... Valve hole 35 ... Caulking part 36 ... Fixed part (fixed piece)
39... Discharge valve (second discharge valve)

Claims (3)

A cylinder block (10), and a piston (17) that is reciprocally fitted in a cylinder hole (15) of the cylinder block (10) to define a pump chamber (23) in the cylinder hole (15); A vibration source (19) for applying reciprocating motion to the piston (17), a discharge chamber (26) adjacent to the pump chamber (23), a suction port (24) provided in the piston (17), and a piston ( 17) Inhalation that opens and closes the suction port (24) and the pump chamber (23) in response to the reciprocating motion of 17) to generate a gas flow in one direction from the suction port (24) to the pump chamber (23). The pump chamber (23) and the discharge chamber (26) are opened and closed according to the reciprocating motion of the valve (25) and the piston (17), and the pump chamber (23) and the discharge chamber (26) are moved in one direction. Discharge valve (3 In) the vibrating compressor comprising,
A valve seat member (30) fixed to the head of the piston (17) facing the pump chamber (23) and having a valve hole (34) opening in the suction port (24) in the center, The suction valve (25) is composed of a valve plate (31) made of a thin steel plate fixed to the valve seat member (30) so as to form a substantially flat surface together with the end surface, and the valve plate (31) An annular support portion (31a) fixed to the outer peripheral portion of the valve seat member (30), a valve portion (31b) for opening and closing the valve hole (34), and an arc shape concentric with the valve portion (31b) A plurality of elastic arm portions (31c) for connecting the support portion (31a) and the valve portion (31b), and provided on both sides of the elastic arm portions (31c) to open the valve portion (31b). And a slit (31d) for connecting between the valve hole (34) and the pump chamber (23). Vibrating compressor, characterized in that. The vibration type compressor according to claim 1,
The said valve seat member (30) is accommodated in the recessed part (33) formed in the head end surface of a piston (17), and this valve seat member (30) is the cyclic | annular form protruded from the internal peripheral surface of piston (17). A caulking portion (35) penetrating the inner peripheral side of the projection (32) is formed, and the caulking portion (35) is caulked outward in the radial direction, and the caulking portion (35) and the valve seat member (30) A vibration type compressor having the annular protrusion (32) sandwiched therebetween. The vibration type compressor according to claim 1 or 2,
A fixing portion (36) protruding in the radial direction from the outer periphery of the support portion (31a) is extended, and the outer peripheral portion of the valve seat member (30) is held by the fixing portion (36), thereby the support portion. (31a) A vibration type compressor having the valve seat member (30) fixed thereto.

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