Damper and method for assembling the damper

Abstract

A damper (1) comprising: a cylinder (2) in which a working fluid is encapsulated; a piston (5) which is slidably housed in the cylinder (2); a piston rod (6) which is connected to the piston (5) and extends to an outside of the cylinder (2); and a damping force-generating mechanism (31) comprising a damping valve (32) which generates a damping force by regulating a flow of the working fluid which is generated during the sliding movement of the piston (5) in the cylinder (2), wherein the damping force-generating mechanism (31) comprises: a coil housing (61) in which a coil (61A) is housed and which has an axial opening (64); a housing element (71) in which the coil housing (61) is provided on an opening side on one side of the housing element (71) and the damping valve (32) is provided on the other side;a plunger (75) provided in the axial opening (64) of the coil housing (61) and which controls the damping force of the damping valve (32) while being moved in an axial direction of the axial opening (64) by the excitation of the coil (61A); and a retaining ring (91) which is provided between a groove (93) formed in an outer circumferential surface (92) of the coil housing (61) and a groove (95) formed in an inner circumferential surface (94) of the housing element (71), so that the coil housing (61) and the housing element (71) are integrated, wherein a sealing element (85) is provided between the coil housing (61) and the housing element (71) such that the sealing element (85) is positioned closer to the opening side of the housing element (71) than the groove (95) of the housing element (71);and wherein the sealing element (85) is sandwiched between a conical bore (84) formed in the housing element (71) and whose diameter increases towards the opening, and the outer circumferential surface of the coil housing (61) such that the sealing element (85) elastically supports the coil housing (61) with respect to the housing element (71) in a radial direction and in the axial direction of the coil housing (61).

Description

technical field

[0001] The present invention relates to a damper that generates a damping force by controlling the flow of a working fluid in response to a stroke of a piston rod, and the method of assembling the same. background

[0002] Patent Document 1 sets z. B. open a solenoid coil in which a molded coil (coil case) and a solenoid coil main body (housing member) are integrated by a snap ring (retaining ring) formed between a groove formed in an outer peripheral surface of the molded coil and one in an inner peripheral surface of the housing formed groove is attached. Incidentally, in a case where the solenoid coil acts on an actuator configured to control a damping force of a damping force adjustment type damper in a semi-active suspension mounted in a vehicle, there is a problem in that unusual noises are generated from the solenoid coil are generated due to a backlash in a direction along an axis of the solenoid coil (hereinafter referred to as an “axial direction”) due to an axial gap between the retainer ring and the groove, or a degree of flexibility in design of a magnetic circuit restricted.

[0003] In order to eliminate the backlash, it has been proposed to sandwich an O-ring at an outer peripheral position of the retainer ring in the axial direction through the molded coil and the solenoid coil main body. However, as the diameter of the magnetic coil increases in a radial direction (requiring the increase in thickness), the size of the magnetic coil increases. Prior Art DocumentPatent Specification

[0004] Patent Specification 1: International Publication No. WO 2013 / 056579 Disclosure of the invention Problems to be solved

[0005] An object of the present invention is to provide a damper configured to eliminate the axial clearance between a coil case and a case member without increasing the size of the solenoid, and a method of assembling the damper. means of solving the problems

[0006] A damper according to an exemplary embodiment of the present invention includes: a cylinder in which a working fluid is encapsulated; a piston slidably fitted in the cylinder; a piston rod connected to the piston and extending to an outside of the cylinder; and a damping force generating mechanism including a damping valve that generates a damping force by controlling a flow of working fluid generated by displacement of the piston in the cylinder. The damping force generating mechanism includes: a spool case accommodating a spool and having an axial hole; a case member in which the coil case is provided on an opening side on one side of the case member and the damper valve is provided on the other side; a plunger that is provided in the axial hole of the spool case and regulates the damping force of the damping valve while moving in an axial direction of the axial hole by energizing the spool; and a retainer ring fixed between a groove formed in an outer peripheral surface of the coil case and a groove formed in an inner peripheral surface of the case member so that the coil case and the case member are integrated. A seal member is provided between the coil case and the case member such that the seal member is positioned closer to the opening side of the case member than the groove of the case member. The sealing member is sandwiched between a tapered bore formed in the case member and whose diameter increases toward the opening, and the outer peripheral surface of the bobbin case so that the sealing member covers the bobbin case with respect to the case member in a radial direction and the axial direction of the bobbin case elastically supported.

[0007] In a method for assembling a damper according to another exemplary embodiment of the present invention, a damping force generating mechanism can be assembled through an assembling process including: integration of the housing member and the damping valve; Use of the integrated housing element and damping valve in a valve housing; and inserting the coil housing into the body member integrated with the valve body.

[0008] According to the damper and the method of assembling the damper according to the exemplary embodiments of the present invention, it is possible to eliminate the axial clearance between the coil case and the case member without increasing the size of the solenoid coil. Brief description of the drawings

[0009] figure 1 is a cross section of a damper according to the present exemplary embodiment, taken along a uniaxial plane.

[0010] figure 2 is a cross section of a damping force generating mechanism according to the present exemplary embodiment, taken along a uniaxial plane.

[0011] figure 3 is a cross section of a coil case taken along a uniaxial plane according to the present exemplary embodiment.

[0012] figure 4 is a cross section of a case member according to the present exemplary embodiment, taken along a uniaxial plane.

[0013] figure 5 is a front view and a top plan view of a retaining ring according to the present exemplary embodiment.

[0014] figure 6 is an explanatory view of the present exemplary embodiment, illustrating a method of assembling a damping force generating mechanism (solenoid). Detailed description for carrying out the invention

[0015] An exemplary embodiment of the present invention will be described with reference to the attached drawings. Furthermore, in the following description, an up and down direction is used in figure 1 as an up and down direction, as is the state of the art.

[0016] As in figure 1 illustrates a damping force regulation type damper 1 , which is a damper according to the present exemplary embodiment, has a multi-cylinder structure in which an outer cylinder 3 outside of a cylinder 2 is provided, and a reservoir 4 between the cylinder 2 and the outer cylinder 3 is formed. A piston 5 can be moved in the cylinder 2 housed, and the interior of the cylinder 2 is through the piston 5 subdivided into two chambers - an upper cylinder chamber 2A and a lower cylinder chamber 2B . One end of a piston rod 6 is with the piston 5 through a mother 7 connected, and the other end of the piston rod 6 runs through the upper cylinder chamber 2A and is through a rod guide 8 and an oil seal 9 introduced at the upper end portions of the cylinder 2 and the outer cylinder 3 is attached so that the other end of the piston rod 6 to the outside of the cylinder 2 extends.

[0017] Furthermore, a bottom valve 10 , which is the lower cylinder chamber 2B and the reservoir 4 separates from each other in a lower end portion of the cylinder 2 intended. The passages 11 and 12 , which connects the upper cylinder chamber 2A and the lower cylinder chamber 2B enable each other are in the flask 5 educated. A check valve 13 , which allows the oil (working liquid) only from the side of the lower cylinder chamber 2B to the side of the upper cylinder chamber 2A flows is in the passage 12 intended. Also, is in transit 11 a disk valve 14provided that the pressure of the oil on the side of the upper cylinder chamber 2A to the side of the lower cylinder chamber 2B degrades towards by being opened when the pressure reaches a predetermined pressure value.

[0018] The passages 15 and 16 , which allow the lower cylinder chamber 2B and the reservoir 4 communicating with each other are in the bottom valve 10 educated. A check valve 17 , which ensures that the oil only from the side of the reservoir 4 to the side of the lower cylinder chamber 2B flows is in the passage 15 intended. Also, is in transit 16 a disk valve 18 provided that the pressure of the oil on the side of the lower cylinder chamber 2A to the side of the reservoir 4 degrades towards by being opened when the pressure reaches a predetermined pressure value. Furthermore, the oil is in the cylinder as the working fluid 2 encapsulated, and the oil and gas are in the reservoir 4 encapsulated.

[0019] A separating tube 20 is on both the top and bottom end portions of the cylinder 2 through the sealing elements 19 placed, and an annular passage 21 is between the cylinder 2 and the separating tube 20 educated. The annular passage 21 stands with the upper cylinder chamber 2A through a passage 22 in connection, which is in a side wall near the upper end portion of cylinder 2 is provided. A cylindrical branch pipe 23 moving laterally (in a right direction in figure 1) protrudes is on a lower side of the separator tube 20 educated. an opening 24 , which has a larger diameter than the branch pipe 23 , is so in the side wall of the outer cylinder 3 designed to be concentric with the branch pipe 23 is, and a cylindrical valve housing 25 is connected by welding or similar in such a way that the opening 24 surrounds. A mechanism generating a damping force 31 is in the valve body 25 accommodated.

[0020] (Damping force generating mechanism) How figure 1 illustrates is the damping force generating mechanism 31 provided so that a bottom end side (left end side in figure 1) the damping force generating mechanism 31 so present that they are between the reservoir 4 and the annular passage 21 is inserted, and the tip end side (the right end side in figure 1) the damping force generating mechanism 31 stands radially outward (in the right direction in the left and right direction in figure 1) from the outer cylinder 3 before. The damping force generating mechanism 31 generates a damping force by controlling a flow of the oil from the annular passage 21 to the reservoir 4 by using a damping valve 32 . In addition, the generated damping force is variably controlled by controlling a valve opening pressure of the damping valve 32 by a magnetic coil 33 (see description below) applied as a variable damping force actuator.

[0021] As in figure 2 illustrates the damping force generating mechanism 31 : the above valve body 25 ; a passage element 34 , the one on the branch pipe 23 of the separating tube 20 at its bottom end side (left end side in figure 2) and a ring-shaped one on the top side of which (the right end side in figure 2) formed flange portion 34A and is provided to have a gap with respect to an inner flange portion 25A at a bottom end side of the valve body 25 having; and a valve element 35 , the one with the flange section 34A of the passage element 34 has contact. A threaded section 39 is at a tip end side of the valve body 25 formed, and the valve housing 25 and the housing element 71the magnetic coil 33 are connected to each other by a threaded portion 39 screw-coupled nut 38 connected with each other. There is also an annular passage 40 , the one with the reservoir 4 communicates between an inner peripheral surface of the valve housing 25 and the damping valve 32 educated.

[0022] A pass 41 , whose one side with the annular passage 21 is in connection and the other side to the valve element 35 extends is inside the passage member 34 educated. Also is an annular spacer 42 sandwiched between the flange portion 34A of the passage element 34 and the inner flange portion 25A of the valve body 25 arranged. A variety of passes 43 , which is a connection between the passage 40 and the reservoir 4 allows is in the spacer 42 educated.

[0023] The valve element 35 has a multitude of passages 44 on which so around an axial opening 35A are provided to be spaced from each other in a circumferential direction. One page (left page in figure 2) each of the passages 44 is with the passage 41 of the passage element 34 in connection. Also, the face on the other side (right side in figure 2) of the valve element 35 an annular concave portion 35B , which is designed so that the opening on the other side of the passage 44 is surrounded, and a ring-shaped seating area 46 on, outside of the annular concave portion 35B is positioned in the radial direction so that a main disc valve 45 on the annular seating area 46 seated or separated from him. Furthermore, the passage allows 44 of the valve element 35 the oil flow between the lateral passage 41 of the annular passage 21 and the side passage 40 of the reservoir 4 through the main disk valve 45 .

[0024] An inner peripheral side of the main disc valve 45 is sandwiched between the valve member 35 and a large diameter portion 47A a guide pin 47 arranged, and an outer peripheral side of the main disc valve 45 sits on the seating area 46 of the valve element 35 on. An annular sealing element 48 is at the rear outer peripheral portion of the main disc valve 45 appropriate. Furthermore, the main disc valve 45 opened when the main disc valve 45 from the seating area 46 is separated by making a pressure on the side of the passage 44 (side of the annular passage 21 ) of the valve element 35 is obtained, thereby allowing the passage 44 (annular passage 21 ) of the valve element 35 with the passage 40 (Reservoir 4 ) is connected.

[0025] The guide pin 47 is formed in a stepped cylindrical shape defining the section 47A having the large diameter in an intermediate area in the axial direction, and at an end portion of the axial hole 47B is an estuary 49 educated. An end page (left end page in figure 2) of the guide pin 47 is in the axial opening 35A of the valve element 35 press fitted so that the main disc valve 45 sandwiched between the section 47A with large diameter and the valve element 35 placed as described above. The other end side (right end side in figure 2) of the guide pin 47 is in an axial opening 50A a pilot body 50 fitted. In this state, a passage 51 , which extends in the axial direction, between the axial opening 50A of the pilot body 50and the other end side of the guide pin 47 educated. The passage 51 is with a back pressure chamber 52 connected between the main disk valve 45 and the pilot body 50 is formed.

[0026] The pilot body 50 is formed in a substantially bottomed cylindrical shape and has a cylindrical portion 50B which has a stepped bore formed therein and a bottom portion 50C having, of the cylindrical portion 50B blocked, and the above axial opening 50A , in which the other end side of the guide pin 47 is fitted is in the bottom section 50C educated. A protruding cylindrical section 50D , which is positioned on an outer diameter side and toward the valve element 35 protrudes over the entire circumference, at one end side (left end side in figure 2) of the bottom section 50C of the pilot body 50 educated. The sealing element 48 of the main disk valve 45 is on the inner peripheral surface of the protruding cylindrical portion 50D attached in a liquid-tight manner, so that the back pressure chamber 52 between the main disc valve 45 and the pilot body 50 is formed. The internal pressure in the back pressure chamber 52 is on the main disk valve 45 applied in one direction, in which the main disc valve 45 is closed, d. H. in a direction in which the main disc valve 45 on the main area 46 of the valve element 35 sits up

[0027] A seating area 54 , which is designed so that it has the axial opening 50A so surrounds that a control valve element 53 seated on it or separated from it, on the other end side (right end side in figure 2) of the bottom section 50C of the pilot body 50 intended. In addition, a return spring 55 showing the control valve element 53 biases in a direction in which the control valve element 53 from the seating area 54 of the pilot body 50 is moved away; a disk valve 56 , which is a fail-safe valve when the solenoid 33 is not energized (when the control valve element 53 maximum from the seating area 54 is spaced); and a retaining plate 57 , having a passage formed therein 57A has, inside the cylindrical portion 50B of the pilot body 50 intended.

[0028] A cap 58 is at an opening end of the cylindrical portion 50B of the pilot body 50 adjusted and fixed thereto in a state where the return spring 55 , the disk valve 56 , the retaining plate 57 etc. inside the cylindrical section 50B available. passages 59 are in the cap 58 formed at four points in the circumferential direction, for example, to serve as flow paths allowing flow of the oil passing through the passage 57A the holding plate 57 to the magnetic coil 33 has flowed, to the passage 40 (Reservoir 4 ) enable through them.

[0029] The control valve element 53 puts together with the pilot body 50 represents a control valve. The control valve element 53 is formed in a substantially cylindrical shape, and the tip end portion of the control valve element 53 that's on the seating area 54 of the pilot body 50 seated or separated therefrom is formed in a conical shape with a narrow end. One end of an actuating pin 69 the magnetic coil 33 is stuck in the control valve element 53 fixed, and the valve opening pressure of the control valve element 53 is in response to energization of the solenoid coil 33 regulated. There is also a flange section 53A , which serves as a spring bearing, over the entire circumference on the bottom end side (right end side in figure2) of the control valve element 53 educated. If the magnetic coil 33 is not aroused, d. H. when the control valve element 53 maximum from the seating area 54 is spaced, comes the flange portion 53A so in contact with the disc valve 56 that it is a fail-safe valve.

[0030] (Solenoid) As in figure 2 illustrates the magnetic coil 33 a coil case 61 and the above case member 71 . As in figure 3 illustrates, the bobbin case 61 formed in a substantially cylindrical shape by compression molding a coil 61A and a core 62 , and a cable 63 is attached to a cable connection section 61B connected, protruding to the radial outside (the upper side in figure 3). The sink 61A creates a magnetic force by feeding an electric current (excitation) through the cable 63 . the core 62 is a member made of a magnetic material and formed in a cylindrical shape having a flange portion at one end thereof 62A having.

[0031] As in figure 4 illustrates is the housing member 71 formed in a substantially cylindrical shape, and a bottom portion 72 , showing an axial opening 72A is formed at an intermediate position in the axial direction (left and right directions in figure 4). A large diameter section 76A a cap 76 , which consists of a stator core made of a non-magnetic material 73 , a core 74 and a pestle 75 covered, is in the axial opening 72A of the bottom section 72 of the housing element 71 fitted. The cap 76 is formed into a substantially bottomed cylindrical shape by deep drawing, and the stator core 73 is at a tip end portion (a bottom portion having a drawn shape) of the cap 76 educated. In addition, the pestle 75 slidable in an inner circumference of the cap 76 inserted in which the ram 75 is provided so that a gap in the axial direction with the stator core 73 is formed. Furthermore, an outer periphery of the core 74 at the inner periphery of the large-diameter portion 76A the cap 76 customized. Furthermore, the side of the damping valve 32 (left end in figure 4) of the ram 75 slidable in a concave section 74B , which is in an end face of the core 74 is formed, attached.

[0032] A flange section 74A is at the side end of the dampening valve 32 (left end in figure 4) of the core 74 educated. An outer peripheral surface of the flange portion 74A and a peripheral edge portion of a surface of the core 74 on one side of the dampening valve 32 opposite side (right side in figure 4) are with the housing element 71 in contact. Also, the cap 58 of the damping valve 32 in contact with the side surface of the damping valve 32 of the flange section 74A of the core 74 . Furthermore, a flange portion 76B the cap 76 in close contact with a surface of the core 74 on the damping valve 32 opposite side. The flange section B of the cap 76 is sandwiched between an annular concave portion 72B , which is in the side surface of the damping valve 32 of the bottom section 72 of the housing element 71 is formed, and the flange portion 74A of the core 74 arranged. Furthermore, an area between the housing member 71 and the cap 76 through an O-ring 77 sealed. Also, the O-ring 77 housed in an annular space defined by a C-chamfer of the axial opening 72A of the bottom section 72of the housing element 71 is formed.

[0033] Meanwhile, the actuation pin mentioned above is 69 supported so that it moves in the axial direction (left and right direction in figure 4) through one on the stator core 73 set sleeve 78 and one on the core 74 set sleeve 79 is movable. The actuating pin 69 is with the pestle 75 by a ring element 80 tied together. The pestle 75 , which is called the moving iron core, is used e.g. B. formed in a substantially cylindrical shape by an iron-based magnetic body, and when the coil 61A is excited so that the magnetic force is generated, the plunger 75 from the core 74 attracted so that a thrust is generated. Furthermore, an axial opening 75A of the pestle 75 formed in a conical shape with a diameter equal to that of the ring member 80 to the side of the stator core 73 (right side in figure 4) increases. As such, the plunger 75 a small thickness in one the core 62 adjacent portion through which exchange of magnetic force is easy, and has a large thickness in a portion between the plunger 75 and the core 74 on, through which the exchange of magnetic force is difficult when the plunger 75 is moved upwards. Therefore, weight reduction of the plunger 75 allows without impeding the exchange of magnetic force, resulting in improved responsiveness.

[0034] As in figure 2 illustrates the cap 76 in an axial opening 64 of the bobbin case 61 inserted in the state in which the bobbin case 61 and the housing element 71 are integrated. In this case, the inside perimeter of the cap 76 inserted plunger 75 positioned so that it faces the core 62 in the bobbin case 61 through the cap 76 is facing. Furthermore, an annular groove 82 , designed to accommodate an O-ring 81 is configured, in the outer peripheral surface of the side end of the damping valve 32 (left end page in figure 2) of the housing element 71 formed, and a portion between the inner peripheral surface of the valve housing 25 and the outer peripheral surface of the case member 71 is held in a liquid-tight manner by the O-ring 81 sealed.

[0035] (Retaining ring) Next, a connection structure between the coil case 61 and the housing element 71 that by a retaining ring 91 is implemented (see figure 5), described.

[0036] As in figure 2 are the bobbin case 61 (shank) and the housing member 71 (opening) by being connected to each other by means of the retaining ring 91 integrated. The retaining ring 91 is between the annular groove 93 that in the outer peripheral surface 92 of the bobbin case 61 is formed, and the annular groove 95 , which in the inner peripheral surface 94 of the housing element 71 is formed, attached. i.e. the retaining ring 91 prevents relative movement between the bobbin case 61 and the housing element 71 in the axial direction (left and right direction in figure 2).

[0037] As in figure 3 illustrated is the groove 93 of the bobbin case 61 closer to the side of the cable connection section 61B (right side in figure 3) positioned as the coil 61A . In addition, the flange portion extends 62A of the core 62 up to near the groove 93 . Therefore, the flange portion A of the core 62 receiving a force on the ground section 93A the groove 93 applied when the diameter of the in the groove 93 of the bobbin case 61 attached retaining ring 91 is reduced, and consequently it is possible to reduce the deformation of the bobbin case61 to prevent. Furthermore, the shape and dimension of the groove 93 of the bobbin case 61 (shank) and the shape and dimension of the groove 95 of the housing element 71 (opening) in relation to e.g. B. Determine the shape and dimension of the groove of the concentric retaining ring for the C-shaped opening according to JISB2804.

[0038] As in figure 5 illustrates the retaining ring 91 formed in a substantially C-shape and has cut ends 96 that cross within a specified range. The sections 97A and 97B small diameter and a section 97C small diameters having a radius of curvature smaller than a radius of the bottom portion 93A (groove bottom circle) of the groove 93 of the bobbin case 61 , will be near the ends 96A and 96B of the retaining ring 91 and at one of the cut ends 96 opposite side (left side in figure 5) formed. The radius of curvature of the sections 97A and 97B small diameter is smaller than the radius of curvature of the section 97C with small diameter. In addition, shank side contact portions 98A and 98B , which have a substantially straight shape, in the retaining ring 91 on both sides of the section 97A formed with a small diameter in the circumferential direction, and the shank side contact portions 99A and 99B , which have a substantially straight shape, on both sides of the section 97B formed with a small diameter in the circumferential direction.

[0039] As in figure 5 are the shank side contact portions 98A and 98B and the shank side contact portions 99A and 99B in external contact with the bottom portion 93A (groove bottom circle) of the groove 93 of the bobbin case 61 (Shank) in a state where the retaining ring 91 between the groove 93 of the bobbin case 61 and the groove 95 of the housing element 71 is attached. In this state are the small-diameter portions 97A , 97B and 97C of the retaining ring 91 in internal contact with a bottom portion 95A (groove bottom circle) of the groove 95 of the housing element 71 (Opening).

[0040] As in figure 4 illustrated, is also a conical bore 84 , whose diameter toward the opening 83 increases and that of the inner peripheral surface 94 is continuously formed in the inner peripheral surface 94 of the housing element 71 near the opening 83 is formed, and an R-shape whose radius is larger than a standard (specified) chamfering amount is formed at the contact portions of the retainer ring 91 formed, with the conical bore 84 of the housing element 71 come into contact when the bobbin case 61 into the housing element 71 is inserted, d. H. the sections 97A , 97B and 97C with small diameter. Therefore, it is possible to damage the tapered bore 84 to avoid acting as a sealing surface of an Ô ring 85 (Sealing member) is used, which will be described later. i.e. the retaining ring 91 does not come into contact with a corner portion of the tapered bore 84 of the housing element 71 , if the bobbin case 61 into the housing element 71 is inserted.

[0041] As in figure 2 illustrates a portion between the bobbin case 61 and the housing element 71 through the O-ring 85 sealed by an annular seal carrier portion 86 is supported. The seal carrier section 86 is through the conical bore 84 , which in the inner peripheral surface 94 of the housing element 71 is formed, and an annular sealing groove 87 that in the outer peripheral surface 92 of the bobbin case 61is formed, configured. As in figure 3 illustrates the seal groove 87 on one side (right side in figure 3) formed by the coil 61A regarding the groove 93 is opposite, in which the retaining ring 91 is attached. Furthermore, the distance from the axial opening 64 (Axis of the bobbin case 61 ) up to the seal groove 87 in the bobbin case 61 approximately equal to the distance from the axial opening 64 to the groove 93 . In other words, is the distance from the axial opening 64 (Axis of the bobbin case 61 ) to the O-ring 85 approximately equal to the distance from the axial opening 64 to the retaining ring 91 in a state where the bobbin case 61 and the housing element 71 are integrated.

[0042] In addition, the sealing groove 87 formed to have a substantially V-shaped cross section and has an annular wall portion 88 , which is parallel to a plane that corresponds to the axis of the axial opening 64 (Axis of the bobbin case 61 ) runs at right angles, as well as a tapered shaft 89 on. The diameter of the tapered shank 89 takes from an inner peripheral side of the wall portion 88 towards one side (right side in figure 3) to that of the groove 93 is opposite. As in figure 2 illustrated is the tapered shank 89 of the bobbin case 61 also parallel to the conical bore 84 of the housing element 71 in the condition in which the bobbin case 61 and the housing element 71 are integrated. Furthermore, in the state in which the bobbin case 61 and the housing element 71 are integrated, the O-ring 85 in the radial direction and the axial direction between the tapered bore 84 and the tapered shaft 89 elastically supported (pressed), and as a result, the reaction force of the elastically deformed O-ring 85 in the axial direction to the side wall portion 88 the sealing groove 87 of the bobbin case 61 applied.

[0043] (Operation) Next, an operation of the above-mentioned damper 1 described by the damping force regulation type.

[0044] The damper 1 of damping force regulation type is attached between the upper and lower sides of a spring of a suspension system of a vehicle. When vibration occurs in the up and down directions due to unevenness of a road surface while the vehicle is running, the damper damps 1 the vibration of the vehicle in a manner in which the piston rod 6 is shifted and from the outer cylinder 3 is extended and retracted and the damping force by the damping force generating mechanism 31 is produced. In this case, an electric current value of the coil 61A the magnetic coil 33 controlled by a control device to the valve opening pressure of the control valve element 53 to regulate, and as a result, the through the damper 1 generated damping force can be variably controlled.

[0045] During an extension stroke of the piston rod 6 becomes the check valve 13 of the piston 5 by the movement of the piston 5 in the cylinder 2 closed, and the oil (working fluid) in the upper cylinder chamber 2A is pressurized before the butterfly valve 14 is opened. The pressurized oil runs through the passage 22 and the annular passage 21 and it flows into the passage member 34 of the mechanism generating the damping force 31 from the branch pipe 23 of the separating tube 20 . In this case, the oil opens according to the amount of movement of the piston 5 the check valve 17 of the bottom valve 10 and it flows from the reservoir 4 in the lower cylinder chamber 2B . When the pressure in the upper cylinder chamber 2Athe valve opening pressure of the butterfly valve 14 of the piston 5 reached, the disc valve is also reached 14 opened and the pressure in the upper cylinder chamber 2A becomes the lower cylinder chamber 2B relieved towards, causing an excessive increase in pressure in the upper cylinder chamber 2A prevented.

[0046] Meanwhile, during the retracting stroke of the piston rod 6 the check valve 13 of the piston 5 by the movement of the piston 5 in the cylinder 2 opened, and the check valve 17 in passage 15 of the bottom valve 10 will be closed. Before the disk valve opens 18 the oil in the lower piston chamber continues to flow 2B in the upper cylinder chamber 2A , and the oil by volume in the cylinder 2 inserted piston rod 6 corresponds, flows into the reservoir 4 from the upper cylinder chamber 2A via the same path used for the extension stroke. Furthermore, the disc valve 18 opened when the pressure in the lower cylinder chamber 2B the valve opening pressure of the butterfly valve 18 of the bottom valve 10 reached, and the pressure in the lower cylinder chamber 2B is in the reservoir 4 relieved, causing an excessive increase in pressure in the lower cylinder chamber 2B is prevented.

[0047] On the other hand, the oil flowing in the damping force generating mechanism 31 before the main disk valve opens 45 (Low speed range of the piston) into the passage 41 of the passage element 34 flows through the axial opening 35A of the valve element 35 , the axial opening 47B of the guide pin 47 and the axial opening 50A of the pilot body 50 , pushes and opens the control valve element 53 and flows into the pilot body 50 . That in the pilot body 50 flowing oil flows between the flange portion 53A of the control valve element 53 and the disk valve 56 and through the passage 57A the holding plate 57 , the passage 59 the cap 58 and the passage 40 of the valve body 25 and then flows into the reservoir 4 . When the speed of the piston increases and the pressure in the passage 41 of the passage element 34 , i.e. H. the pressure in the upper cylinder chamber 2A , the valve opening pressure in the main disk valve 45 reached, it flows into the passage 41 of the passage element 34 flowing oil through the passage 44 of the valve element 35 , pushes and opens the main disk valve 45 , passes through the passage 40 of the valve body 25 and then flows into the reservoir 4 .

[0048] Therefore, during the extension stroke and retraction stroke of the piston rod 6 the damping force through the muzzle 49 of the guide pin 47 and the valve opening pressure of the control valve element 53 generated before the main disk valve 45 of the damping valve 32 is opened, and the damping force is increased in response to an opening degree of the main disk valve 45 after the opening of the main disc valve 45 generated. In this case, the damping force can be controlled directly, regardless of the piston speed, by adjusting the valve opening pressure of the control valve element 53 by supplying an electric current to the coil 61A the magnetic coil 33 is regulated.

[0049] In particular, when attached to the coil 61A delivered electric current is diminished, so that the thrust of the ram 75 is reduced, the valve opening pressure of the control valve element 53 is reduced and as a result, the damping force is generated on a soft side. On the other hand, when connected to the coil 61A delivered electric current is increased, so that the thrust of the ram 75 is increased, the valve opening pressure of the control valve element 53is increased and as a result, the damping force is generated on a hard side. In this case, the internal pressure in the back pressure chamber 52 , the connection to the passage 51 on an upstream side by the valve opening pressure of the control valve element 53 changed. It is therefore possible to increase the valve opening pressure of the main disc valve 45 to regulate simultaneously by the valve opening pressure of the control valve element 53 is controlled, and as a result, the damping force characteristics can be largely controlled.

[0050] In addition, in the event of a loss of thrust of the ram 75 in the event of a failure such as B. Coil detachment 61A or failure of a vehicle mounted control device, the control valve element 53 by the spring force of the return spring 55 withdrawn to the passage 60 of the pilot body 50 to open, and the flange section 53A of the control valve element 53 will be in contact with the disc valve 56 (Fail-safe disc valve) brought so that a flow path between a valve chamber 67 and the passage 40 in the valve body 25 is closed. In this condition, the flow of oil from the passage 60 into the passage 40 in the valve body 25 through the disc valve 56 in the valve chamber 67 is regulated, and as a result, a desired damping force can be obtained by reducing the valve opening pressure of the disc valve 56 and the internal pressure in the back pressure chamber 52 to be set, d. H. the valve opening pressure of the main disc valve 45 can be regulated. As a result, an appropriate damping force can be obtained even if a failure occurs.

[0051] (Assembling Method) Next, a method for assembling a damper 1 of the damping force regulation type of the present exemplary embodiment will be described. Here, a method for assembling the damping force generating mechanism 31 in relation to figure 6 described.

[0052] First, the housing element 71 and the damping valve 32 integrated. Here's the cap 76 , in which the stator core 73 , the core 74 , the pestle 75 and the actuating pin 69 be set in advance, in the housing member 71 . In this state, the stator core 73 , the core 74 , the pestle 75 and the actuating pin 69 coaxial with respect to the housing member 71 positioned.

[0053] Next will be the housing element 71 and the damping valve 32 that are integrated into the valve body 19 deployed. Furthermore, the mother 38 with the threaded section 39 of the valve body 25 screw coupled and the nut 38 is tightened so that the valve body 25 , the damping valve 32 and the housing element 71 are integrated. Furthermore, the valve housing 25 on the side wall of the outer cylinder 3 bonded in advance (see figure 1).

[0054] Next up is the bobbin case 61 from the opening 83 of the housing element 71 , which is on the valve body 25 is fixed, in the housing member 71 plugged in. In this case, the retaining ring 91 in the groove 93 of the bobbin case 61 attached in advance, and the O-ring 85 (sealing element) is placed in the sealing groove 87 of the bobbin case 61 fastened. Also, during the process of inserting the bobbin case 61 the diameter of the retaining ring 91 , the one in the groove 93 of the bobbin case 61 attached, gradually decreased while the retaining ring 91 on the conical hole 84 of the housing element 71 is pushed, and the diameter of the retaining ring 91 is increased when the retaining ring 91 the groove 95 of the housing element 71facing so that the retaining ring 91 in the groove 95 is attached, d. H. between the groove 93 of the bobbin case 61 and the groove 95 of the housing element 71 is attached. Next come the shank side contact portions 98A and 98B and the shank side contact portions 99A and 99B of the retaining ring 91 in contact with the bottom section 93A the groove 93 of the bobbin case 61 .

[0055] Furthermore, when using the bobbin case 61 the diameter of the retaining ring 91 decreases when the small-diameter portions 97A , 97B and 97C (please refer figure 5) in contact with the conical bore 84 of the housing element 71 come; however, the R-shape whose radius is larger than the standardized fraying amount is formed on a portion in contact with the tapered bore 84 in each of the small-diameter portions 97A , 97B and 97C should be, and as a result it is possible to damage the tapered bore 84 , which acts as the sealing surface of the O-ring 85 (Sealing element) serves to prevent. Furthermore, the sliding resistance between the retaining ring 91 and the conical bore 84 when using the bobbin case 61 reduced, and as a result it is possible to place one on the bobbin case 61 to reduce applied force and the deformation of the bobbin case 61 to prevent. Therefore, it is possible the deformation of the bobbin case 61 and the deformation of the seal groove 87 to prevent acting as the sealing surface of the O-ring 85 serves, thereby preventing deterioration of the sealability.

[0056] Meanwhile, during the inserting process of the bobbin case 61 the o ring 85 , which is in the seal groove 87 of the bobbin case 61 is attached through the conical bore 84 of the housing element 71 and the tapered shank 89 of the bobbin case 61 , which is the O-ring 85 approach, compressed (compressed) while maintaining the parallel state, and finally the O-ring 85 in the radial direction and the axial direction between the tapered bore 84 and the tapered shaft 89 elastically supported. In this state, the wall section 88 the sealing groove 87 of the bobbin case 61 by a reaction force of the elastic force generated by the elastically deformed O-ring 85 is generated is pushed in the axial direction. Therefore, an axial force between the bobbin case 61 the magnetic coil 33 and the housing element 71 generated, and as a result, it is possible to reduce the axial clearance between the bobbin case 61 and the housing element 71 to prevent.

[0057] Furthermore, the cap 76 of the housing element 71 into the axial opening 64 of the bobbin case 61 used in a state where the bobbin case 61 is fully inserted, and as a result, the bobbin case 61 and the housing element 71 be reliably positioned coaxially, and the bobbin case 61 , the pestle 75 and the actuating pin 69 can be reliably positioned coaxially. Also, the cap 76 through the O-ring 77 with regard to the housing element 71 aligned, and the bobbin case 61 is through the O-ring 85 with regard to the housing element 71 aligned, and as a result, the corresponding elements can each through the O-rings 77 and 85 be aligned.

[0058] (Effect) According to the present exemplary embodiment, the coil case 61 during the assembly process of the magnetic coil 33 into the housing element 71 inserted so that the retaining ring 91 between the groove93 that in the outer peripheral surface 92 of the bobbin case 61 is formed, and the groove 95 , which in the inner peripheral surface 94 of the housing element 71 is formed, is inserted, and as a result, the bobbin case 61 and the housing element 71 integrated. In the state where the bobbin case 61 and the housing element 71 are integrated, the O-ring 85 (sealing element) through the conical bore 84 , which in the inner peripheral surface 94 of the housing element 71 is formed, and the tapered shank 89 , which is on the outer peripheral surface 92 of the bobbin case 61 is formed, elastically supported, and the retaining ring 91 receives the axial force (reaction force of the elastic force) coming from the O-ring 85 is produced.

[0059] Because the retaining ring 91 receives the axial force generated by the O-ring 85 is generated as described above, it is possible to have a clearance between the bobbin case 61 the magnetic coil 33 and the housing element 71 to avoid, thereby preventing from the damper 1 unusual noises are produced. In addition, the O-ring 85 through the conical hole 84 (inclined surface) of the housing member 71 supported and the distance from the axis (centerline) of the solenoid 33 to the retaining ring 91 is approximately equal to the distance from the axis of the magnetic coil 33 to the O ring 85 ; as a result, it is possible to reduce an outer diameter of the case member 71 to reduce (reduce thickness) and the size of the magnetic coil 33 to reduce, particularly the size of the damping force regulating mechanism 31 compared to the prior art in which the O-ring 85 on the lateral end face of the opening 33 of the housing element 71 is recorded, d. H. on a surface parallel to a plane perpendicular to the axis of the solenoid 33 runs.

[0060] In addition, according to the present exemplary embodiment, the R-shape, the radius of which is larger than the standard (specified) chamfering amount, is formed on the portion of the case member 71 formed in contact with the conical bore 84 is, i. H. on the small-diameter portions 97A , 97B and 97C is formed when the retaining ring 91 in the housing element 71 of the bobbin case 61 is used and as a result it is possible to damage the tapered bore 84 , which acts as the sealing surface of the O-ring 85 serves to prevent if the bobbin case 61 during the process of assembling the solenoid 33 is used. Furthermore, the sliding resistance between the retaining ring 91 and the conical bore 84 of the housing element 71 when using the bobbin case 61 reduced, and as a result it is possible that on the bobbin case 61 to reduce applied force and the deformation of the bobbin case 61 to prevent. Therefore, it is possible the deformation of the bobbin case 61 and the deformation of the seal groove 87 to prevent acting as the sealing surface of the O-ring 85 serves, thereby preventing deterioration of the sealability.

[0061] Furthermore, the present exemplary embodiment is configured so that the O-ring 85 (Seal member) in the radial direction and the axial direction through the tapered bore 84 of the housing element 71 and the tapered shank 89 (inclined surface) of the bobbin case 61 is elastically supported, however, the sealing groove needs 87 on the side of the bobbin case 61 no shank designed in a tapering shape 89 (inclined surface) and the seal groove 87 can through the pair of opposite wall sections 88and the bottom portion (groove bottom) parallel to the axis (centerline) of the solenoid 33 runs and through the pair of wall sections 88 is formed continuously can be configured.

[0062] As the damper according to the exemplary embodiment and the assembling method for the damper, the following aspects can be provided as examples.

[0063] A first aspect of a damper includes: a cylinder in which a working fluid is encapsulated; a piston slidably housed in the cylinder; a piston rod connected to the piston and extending to an outside of the cylinder; and a damping force generating mechanism including a damping valve that generates a damping force by controlling a flow of the working fluid generated while the piston slides in the cylinder. The damping force generating mechanism includes: a spool case accommodating a spool and having an axial hole; a case member in which the coil case is provided on an opening side on one side of the case member and the damper valve is provided on the other side; a plunger that is provided in the axial hole of the spool case and regulates the damping force of the damping valve while moving in an axial direction of the axial hole by energizing the spool; and a retainer ring fixed between a groove formed in an outer peripheral surface of the coil case and a groove formed in an inner peripheral surface of the case member so that the coil case and the case member are integrated. A seal member is provided between the coil case and the case member such that the seal member is positioned closer to the opening side of the case member than the groove of the case member. The sealing member is sandwiched between a tapered bore formed in the case member and whose diameter increases toward the opening, and the outer peripheral surface of the bobbin case so that the sealing member covers the bobbin case with respect to the case member in a radial direction and the axial direction of the bobbin case elastically supported.

[0064] According to a second aspect, in the first aspect, the coil case includes a tapered shank formed therein, the diameter of which increases toward the opening side of the case member.

[0065] According to a third aspect, in the second aspect, the tapered bore of the case member and the tapered shank of the coil case are parallel to each other.

[0066] According to a fourth aspect, in any one of the first to third aspects, the tapered bore of the case member is formed continuously from an inner peripheral surface of the case member in which the groove is formed.

[0067] According to a fifth aspect, in any one of the first to fourth aspects, the retaining ring includes a small-diameter portion formed near a tip end thereof and whose radius of curvature is smaller than the radius of a groove bottom of the coil case, and an R-shape whose radius is larger than a standard fraying amount is formed at least on the small-diameter portion at a portion contacting the bobbin case.

[0068] According to a sixth aspect, in a method of assembling the damper according to any one of the first to fifth aspects, the damping force generating mechanism can be assembled through an assembling process including: integration of the housing member and the damping valve; Use of the integrated housing element and damping valve in a valve housing; and inserting the coil housing into the body member integrated with the valve body.

[0069] While only a few exemplary embodiments of the present invention have been described above, it will be readily apparent to those skilled in the art that various changes and modifications can be made in the exemplary embodiments without materially departing from the novel teachings or advantages of the present invention. Therefore, the changed and modified aspects are also intended to be included in the technical scope of the present invention. The exemplary embodiments can be combined with one another as desired.

[0070] The present patent application claims priority based on Japanese Patent Application No. 2015-210969 filed on Oct. 27, 2015. The entire disclosure contents including the specification, claims, drawings and abstract of Japanese Patent Application No. 2015-210969 filed on Oct. 27, 2015 are incorporated herein by reference. Reference List 1 damper 2 cylinders 5 pistons 6 piston rod 31 damping force generating mechanism 32 damping valve 61 bobbin case 61A coil 64 Axial opening (bobbin case) 71 housing element 75 pestle 83 opening 84 Tapered Bore 85 O-ring (sealing element) 91 retaining ring 92 Outer peripheral surface (bobbin case) 93 slots 94 Inner peripheral surface (housing member) 95 slots

Claims

[1] A damper, comprising: a cylinder in which a working fluid is encapsulated; a piston that is slidably housed in the cylinder; a piston rod connected to the piston and extending to an outside of the cylinder; and a damping force-generating mechanism comprising a damping valve that generates a damping force by regulating a flow of working fluid generated during the sliding movement of the piston in the cylinder, the mechanism generating the damping force includes: a coil housing in which a coil is housed and which has an axial opening; a housing element in which the coil housing is provided on an opening side on one side of the housing element, and the damping valve is provided on the other side; a plunger provided in the axial opening of the coil housing, which regulates the damping force of the damping valve while being moved in an axial direction of the axial opening by the excitation of the coil; and a retaining ring that is fitted between a groove formed in an outer circumferential surface of the coil housing and a groove formed in an inner circumferential surface of the housing element, so that the coil housing and the housing element are integrated, wherein a sealing element is provided between the coil housing and the housing element such that the sealing element is positioned closer to the opening side of the housing element than the groove of the housing element; and wherein the sealing element is arranged in a sandwich-like manner between a conical bore formed in the housing element, the diameter of which increases towards the opening, and the outer circumferential surface of the coil housing, such that the sealing element elastically supports the coil housing with respect to the housing element in a radial direction and the axial direction of the coil housing. [2] The damper according to claim 1, wherein the coil housing comprises a tapered shaft formed therein so that the diameter increases towards the opening side of the housing element. [3] The damper according to claim 2, wherein the conical bore of the housing element and the tapered shaft of the coil housing run parallel to each other. [4] The damper according to one of claims 1 to 3, wherein the conical bore of the housing element is continuously formed by an inner circumferential surface of the housing element in which the groove is formed. [5] The damper of one of claims 1 to 4, wherein the retaining ring comprises a small-diameter section formed near a tip end of it, the radius of curvature being smaller than the radius of a groove bottom of the coil housing, and an R-shape, the radius of which is larger than a standardized fraying amount, formed at least on the small-diameter section on a section that is in contact with the coil housing. [6] A method for assembling the damper according to any one of claims 1 to 5, wherein the damping force-generating mechanism is assembled by an assembly process, comprising: Integration of the housing element and the damping valve; Use of the integrated housing element and damping valve in a valve housing; and Insertion of the coil housing into the housing element, which is integrated with the valve housing.