JP4811092B2 - Pump device - Google Patents

Description

  The present invention relates to a pump device that drives a pump via a drive shaft supported by a bearing to suck and discharge fluid.

In the conventional pump device disclosed in Patent Document 1, a drive shaft is inserted into a case, the drive shaft is rotatably supported by a bearing, and a pump housed in the case is driven via the drive shaft. The fluid is sucked and discharged.
JP 2004-52988 A

  However, since the conventional pump device disclosed in Patent Document 1 uses a needle bearing that does not include an inner race as a bearing that supports the drive shaft, the relative movement of the bearing and the drive shaft in the direction of the drive shaft axis. Therefore, it is difficult to prevent the drive shaft from coming off by the bearing. In order to prevent the drive shaft from coming off, a ring-shaped member is fitted on one end of the drive shaft, and a large-diameter portion is formed on the other end of the drive shaft. Therefore, such a separate member (ring-shaped member) is required to prevent the drive shaft from coming off, and the drive shaft becomes longer by that amount in order to secure an outer fitting portion of the ring-shaped member at one end of the drive shaft. There was a problem that.

  An object of the present invention is to provide a pump device capable of reducing the number of parts, shortening the drive shaft, and thus reducing the size of the pump device while ensuring the function of preventing the drive shaft from coming off. .

In order to achieve the above object, according to the first aspect of the present invention, the drive shaft (54) is inserted into the first case (71a-71c), and the drive shaft (54) is supported by the bearings (51, 52). A pump device that rotatably supports a pump (10, 13) housed in a first case (71a-71c) via a drive shaft (54) to suck and discharge fluid. (51) includes an inner race (51c) in which the drive shaft (54) is press-fitted and fixed, and an outer race (51b) disposed in the first case (71a to 71c) in a state in which movement in the direction of the drive shaft is restricted. ) And the inner race (51c) and the outer race (51b), the rolling elements (51d) disposed between the inner race (51c) and the outer race (51b) in a state in which the relative movement in the drive shaft axis direction can be restricted. ) Than the drive shaft axial length of the N'naresu (51c) drive shaft axial length outer race of (51b) and long Kuna' further both the arranged coaxially at the first case (71 a to 71 c) 1 A second case (71d) that can move relative to the cases (71a to 71c) in the drive shaft axis direction, and a first case (71a to 71c) and a second case (71d) disposed between the second case (71d) and the second case (71d). Spring means (210) for urging the first case (71a to 71c) and the second case (71d) away from each other, and the first case (71a to 71c) and the second case (71d) are first. The case (71a-71c) side is inserted into the recess (150a) of the housing (150) with the tip as the tip, and the second case (71d) is directed from the inlet side of the recess (150a) toward the first case (71a-71c). The outer race (51b) is in contact with the end surface of the first case (71a to 71c) facing the bottom surface of the recess (150a) and the bottom surface of the recess (150a). The structure is characterized in that the movement in the axial direction is restricted.

  According to this, the movement of the outer race (51b) in the direction of the drive shaft axis is regulated to position the bearing (51), and the drive shaft (54) is press-fitted and fixed to the inner race (51c) to thereby obtain a bearing ( 51) can restrict the movement of the drive shaft (54) in the direction of the drive shaft axis (that is, prevent the drive shaft from coming off).

  Further, since the inner race (51c) is made longer than the outer race (51b), the press-fit strength of the drive shaft (54) is reduced while suppressing the increase in the size of the outer race (51b) (that is, suppressing the increase in the size of the pump device). Therefore, it is possible to reduce the size of the pump device while improving the reliability of retaining.

Further, by arranging the outer race (51b) so that the movement of the drive shaft (54) can be restricted in both directions (both directions in the drive shaft axis direction), the drive shaft (54) has the above-described conventional configuration. It is not necessary to provide such a large diameter portion, and the shape of the drive shaft (54) can be simplified.
By the way, the distance between the first case (71a to 71c) and the second case (71d) tends to easily change and vary because the spring means is interposed between them. Therefore, for example, when the outer race (52b) is configured to be in contact with the first case (71a to 71c) and the second case (71d) so that the movement of the outer race (52b) in the drive shaft axis direction is restricted. This affects the movement range of the outer race (52b) in the direction of the drive shaft. In that respect, according to the present invention, the outer race (51b) is disposed between the end surface of the first case (71a to 71c) and the bottom surface of the recess (150a), and therefore, it is difficult to be affected. . Therefore, the range of movement of the outer race (51b) in the direction of the drive shaft can be reduced, and as a result, the range of movement of the drive shaft (54) can be reduced.

  According to a second aspect of the present invention, in the pump device according to the first aspect, the outer race (51b) is loosely fitted into the first case (71a to 71c) and the first case (71a to 71c). The structure is characterized in that the movement in the direction of the drive shaft axis is restricted by contact with the end surface in the direction of the drive shaft axis.

  According to this, since the axial movement of the outer race (51b) can be restricted without press-fitting the outer race (51b) into the first case (71a to 71c), the deformation of the first case (71a to 71c) is prevented. Can be prevented.

  In the invention according to claim 3, in the pump device according to claim 1 or 2, the drive shaft (54) is rotatably supported by the plurality of bearings (51, 52), and the plurality of bearings (51, 52). ) In the first case (71a to 71c) with the inner race (51c) in which the drive shaft (54) is press-fitted and fixed and the movement in the direction of the drive shaft is restricted. The outer race (51b) and the inner race (51c) and the outer race (51b) are arranged between the inner race (51c) and the outer race (51b) in a state in which the relative movement in the drive shaft axis direction can be restricted. The inner race (51c) is longer in the drive shaft axial direction than the outer race (51b) in the drive shaft axial direction, and has a plurality of bearings (5 Other bearings (52 out of 52)) is characterized in that the drive shaft axial length of the drive shaft axial length and outer race of the inner race (52c) (52 b) are equal.

  According to this, among the plurality of bearings (51, 52), the other bearings (52) can be made shorter in length in the drive shaft axis direction than some of the bearings (51). Is possible. Further, by adopting a general-purpose bearing for the other bearing (52), an increase in cost can be suppressed.

  Even in this configuration, the length of the inner race (51c) in the drive shaft axis direction is longer than the length of the outer race (51b) in the drive shaft axis direction for the above-mentioned partial bearings (51). The press-fitting strength with respect to the drive shaft (54) is ensured to be high, and the movement of the drive shaft (54) in the axial direction is well regulated.

  According to a fourth aspect of the present invention, in the pump device according to any one of the first to third aspects, the drive shaft (54) is rotatably supported by a plurality of bearings (51, 52). Among the bearings (51, 52), a part of the bearings (51) includes an inner race (51c) in which the drive shaft (54) is press-fitted and fixed, and the first case ( 71a to 71c), the inner race (51c) and the outer race (51b) in a state in which the relative movement of the outer race (51b) and the inner race (51c) and the outer race (51b) in the drive shaft axis direction can be restricted. A length of the inner race (51c) in the drive shaft axial direction is longer than a length of the outer race (51b) in the drive shaft axial direction. Bearings (51, 52) other bearing (52) of the drive shaft to the inner race (52c) (54) is equal to or is clearance fit.

  According to this, since the other bearings (52) among the plurality of bearings (51, 52) can be easily assembled to the drive shaft (54), the assemblability is improved.

According to a fifth aspect of the present invention, in the pump device according to any one of the first to fourth aspects, the pump (10, 13) is constituted by a gear pump housed in the first case (71a-71c). The bearings (51, 52) are constituted by ball bearings, and a drive shaft (54) for driving the gear pumps (10, 13) is rotatably supported by the ball bearings (51, 52). .

  According to this, it is possible to regulate the movement of the drive shaft (54) in the drive shaft axis direction by press-fitting and fixing the drive shaft (54) to the inner race (51c) of the ball bearing (51). The ball bearing (51) can prevent the drive shaft (54) from coming off. Therefore, a retaining member is not required, and the number of parts and the drive shaft (54) can be shortened.

  In addition, the code | symbol in the bracket | parenthesis of each means described in a claim and this column shows the correspondence with the specific means as described in embodiment mentioned later.

  The present invention will be described with reference to embodiments shown in the drawings. FIG. 1 is a view showing a vehicle brake device using a pump device according to an embodiment of the present invention.

  First, the basic configuration of the brake device will be described with reference to FIG. Here, an example in which the brake device according to the present invention is applied to a vehicle that constitutes a hydraulic circuit of an X pipe having a right front wheel-left rear wheel and a left front wheel-right rear wheel piping system in a front wheel drive four-wheel vehicle will be described. However, it can also be applied to front and rear piping.

  As shown in FIG. 1, the brake pedal 1 is connected to a booster device 2, and the brake pedal force and the like are boosted by the booster device 2.

  The booster 2 has a push rod or the like that transmits the boosted pedaling force to the master cylinder 3, and the push cylinder presses a master piston disposed in the master cylinder 3 to thereby master cylinder. Pressure is generated. The brake pedal 1, the booster 2 and the master cylinder 3 correspond to brake fluid pressure generating means.

  The master cylinder 3 is connected to a master reservoir 3 a that supplies brake fluid into the master cylinder 3 and stores excess brake fluid in the master cylinder 3.

  The master cylinder pressure is transmitted to the wheel cylinder 4 for the right front wheel FR and the wheel cylinder 5 for the left rear wheel RL via a brake fluid pressure control actuator that performs ABS control and the like. In the following description, the right front wheel FR and the left rear wheel RL side will be described. However, since the same applies to the left front wheel FL and the right rear wheel RR side which are the second piping system, the description will be omitted.

  The brake device includes a pipe line (main pipe line) A connected to the master cylinder 3, and the pipe line A is provided with a linear differential pressure control valve 22 together with a check valve 22a. The pipe A is divided into two parts by the linear differential pressure control valve 22. That is, the pipeline A includes a pipeline A1 that receives the master cylinder pressure between the master cylinder 3 and the linear differential pressure control valve 22, and a pipeline A2 between the linear differential pressure control valve 22 and the wheel cylinders 4 and 5. It is divided into.

  The linear differential pressure control valve 22 is normally in communication, but when the brake is suddenly applied to the wheel cylinders 4 and 5 when the master cylinder pressure is lower than a predetermined pressure, or during traction control, the master cylinder side and the wheel cylinder It will be in the state (differential pressure state) which generates a predetermined differential pressure between the two sides. The linear differential pressure valve 22 can linearly adjust the set value of the differential pressure.

  Further, in the pipeline A2, the pipeline A is branched into two, and one of the openings is provided with a pressure increase control valve 30 for controlling the increase of the brake fluid pressure to the wheel cylinder 4, and the other is provided. A pressure increase control valve 31 for controlling the increase in brake fluid pressure to the wheel cylinder 5 is provided.

  These pressure increase control valves 30 and 31 are configured as two-position valves that can control the communication / blocking state by an electronic control unit (hereinafter referred to as ECU). When the two-position valve is controlled to be in communication, the master cylinder pressure or the brake fluid pressure generated by pump discharge can be applied to the wheel cylinders 4 and 5. These first and second pressure-increasing control valves 30 and 31 are always controlled to communicate during normal braking when ABS control is not being executed.

  The pressure increase control valves 30 and 31 are provided with safety valves 30a and 31a, respectively, so that brake fluid is removed from the wheel cylinders 4 and 5 side when the brake depression is stopped and the ABS control is finished. It has become.

  The pipe (intake pipe) B connecting the pipe A and the reservoir 40 between the first and second pressure-increasing control valves 30 and 31 and the wheel cylinders 4 and 5 is connected and cut off by the ECU. The pressure-reducing control valves 32 and 33 that can control the above are respectively provided. These pressure reduction control valves 32 and 33 are always cut off in the normal brake state (when the ABS is not operating).

  A rotary pump 13 is disposed in a pipe line (refluxing pipe line) C connecting the linear differential pressure control valve 22 and the pressure increase control valves 30 and 31 in the pipe line A and the reservoir 40. A safety valve 13A is provided on the discharge port side of the rotary pump 13 so that the brake fluid does not flow backward. A motor 11 is connected to the rotary pump 13, and the rotary pump 13 is driven by the motor 11. In addition, the 2nd piping system is equipped with the rotary pump 10 (refer FIG. 2) comprised similarly to the rotary pump 13. As shown in FIG. Details of these rotary pumps 10 and 13 will be described later.

  A conduit (auxiliary conduit) D is provided so as to connect the reservoir 40 and the master cylinder 3. A two-position valve 23 is disposed in the pipeline D, and the two-position valve 23 is normally shut off and the pipeline D is shut off. When the two-position valve 23 is in a communication state at the time of brake assist or traction control and the pipe D is in a communication state, the rotary pump 13 draws the brake fluid in the pipe A1 through the pipe D, The wheel cylinder pressure in the wheel cylinders 4 and 5 is discharged to the pipe line A2 to be higher than the master cylinder pressure to increase the wheel braking force. At this time, the differential pressure between the master cylinder pressure and the wheel cylinder pressure is held by the linear differential pressure control valve 22.

  The reservoir 40 is connected to the pipeline D to receive the brake fluid from the master cylinder 3 side, and the reservoir hole 40a is connected to the pipeline B and pipeline C to receive the brake fluid released from the wheel cylinders 4 and 5. 40b. A ball valve 41 is disposed inside the reservoir hole 40a. The ball valve 41 is provided with a rod 43 having a predetermined stroke for moving the ball valve 41 up and down separately from the ball valve 41.

  Also, in the reservoir chamber 40c, there are a piston 44 that works in conjunction with the rod 43, and a spring 45 that generates a force that pushes the piston 44 toward the ball valve 41 to push out the brake fluid in the reservoir chamber 40c. Is provided.

  In the reservoir 40 configured in this manner, when a predetermined amount of brake fluid is stored, the ball valve 41 is seated on the valve seat 42 so that the brake fluid does not flow into the reservoir 40. Therefore, more brake fluid than the suction capacity of the rotary pump 13 does not flow into the reservoir chamber 40c, and no high pressure is applied to the suction side of the rotary pump 13.

  FIG. 2 is a sectional view of the pump device 100 including the rotary pumps 10 and 13. This figure shows a state in which the pump device 100 is assembled to the housing 150 of the brake fluid pressure control actuator, and is assembled so that the vertical direction on the paper surface is the vehicle vertical direction. Hereinafter, the overall configuration of the pump apparatus 100 will be described with reference to FIG.

  As described above, the brake device includes two systems, the first piping system and the second piping system. For this reason, the pump apparatus 100 includes two rotary pumps 13 for the first piping system shown in FIGS. 1 and 2 and the rotary pump 10 for the second piping system shown in FIG. ing. These rotary pumps 10 and 13 are driven by a single drive shaft 54.

  The case constituting the outer shape of the pump device 100 is constituted by first, second, third, and fourth cylinders 71a, 71b, 71c, and 71d and cylindrical first and second center plates 73a and 73b.

  The 1st cylinder 71a, the 1st center plate 73a, the 2nd cylinder 71b, the 2nd center plate 73b, and the 3rd cylinder 71c are piled up in order, and the circumference of the overlapping part is joined by welding. The welded unitized portion is used as a first case, and a disc spring 210 corresponding to a spring means is sandwiched between the first cylinder and the third cylinder 71c in the first case, and a fourth cylinder corresponding to the second case. 71d is arranged coaxially with respect to the first case. In this way, the integral pump device 100 is configured.

  The pump device 100 having an integral structure as described above is inserted into a substantially cylindrical recess 150a formed in the housing 150 for the brake fluid pressure control actuator.

  Then, a ring-shaped male screw member 200 is screwed into a female screw groove 150b dug in the inlet of the recess 150a, and the pump device 100 is fixed to the housing 150. Specifically, a circular second recess 150 c is formed in the recess 150 a of the housing 150 at a position corresponding to the tip of the drive shaft 54 in the tip position in the insertion direction of the pump device 100. The diameter of the second recess 150c is larger than the drive shaft 54 but smaller than the outer diameter of the first cylinder 71a. For this reason, the tip of the drive shaft 54, that is, the portion protruding from the end surface of the first cylinder 71a enters the second recess 150c, and the portion other than the second recess 150c in the bottom surface of the recess 150a is the first cylinder 71a. The pump device 100 can obtain an axial force by tightening the male screw member 200.

  Here, regarding the structure for fixing the pump device 100 to the concave portion 150a of the housing 150, since the disc spring 210 is provided, the disc spring 210 acts as follows.

  In order to fix the pump device 100 to the housing 150, in other words, to prevent the pump device 100 from rattling inside the housing 150 due to a high brake fluid pressure when the pump device 100 sucks and discharges brake fluid, We must secure power.

  However, if the axial force is obtained only by tightening the male screw member 200, a large variation in the axial force may occur.

  On the other hand, in this embodiment, the disc spring 210 is arrange | positioned between the 3rd, 4th cylinders 71c and 71d, and the edge part by the side of the 3rd cylinder 71c among the 4th cylinders 71d is diameter-reduced, The part is inserted into a third center hole 72c of a third cylinder 71c described later. The diameter of the portion of the fourth cylinder 71d that is inserted into the third center hole 72c of the third cylinder 71c is set to be approximately the same as or slightly smaller than the diameter of the third center hole 72c. The four cylinders 71d are loosely fitted to the third center hole 72c of the third cylinder 71c.

  Therefore, when the male screw member 200 is tightened, the pump device 100 is fixed to the hole 150a of the housing 150 by the elastic force of the disc spring 210 arranged between the fourth cylinder 71d and the third cylinder 71c. Axial force is generated. That is, a member located on the right side of the drawing with respect to the third cylinder 71c is pressed against the bottom surface of the concave portion 150a by the disc spring 210, and the fourth cylinder 71d is pressed against the male screw member 200 side by the disc spring 210. Is generated. Therefore, the axial force can be stabilized, and the axial force applied to the pump device 100 can be minimized without being excessive. Thereby, the deformation | transformation of the pump apparatus 100 can be suppressed.

  The direction of the disc spring 210 is such that the bottom side of the disc spring 210 (the side on which the load is applied to the outer periphery) faces the rotary pumps 10 and 13 and the upper side of the disc spring 210 (the side on which the load is applied to the inner periphery). Is configured to face the motor 11 side.

  The first to fourth cylinders 71a to 71d are provided with first, second, third, and fourth center holes 72a, 72b, 72c, and 72d, respectively.

  A bearing 51 is provided on the inner periphery of the first center hole 72a formed in the first cylinder 71a, and a bearing 52 is provided on the inner periphery of the third center hole 72c formed in the third cylinder 71c. Yes. These bearings 51 and 52 are constituted by ball bearings whose length in the drive shaft axis direction is shorter than that of the needle bearing.

  Specifically, the bearing 51 disposed in the first center hole 72a of the first cylinder 71a has a cylindrical outer race 51b fitted into the step-shaped first center hole 72a. The end surface of the outer race 51b in the direction of the drive shaft axis faces the end surface of the stepped portion of the first center hole 72a and the bottom surface of the recess 150a of the housing 150, and the outer race 51b is the step of the first center hole 72a. The movement in the direction of the drive shaft is regulated by contacting the end surface of the attached portion and the bottom surface of the recess 150a.

  A drive shaft 54 is press-fitted and fixed to the cylindrical inner race 51c. In order to secure the press-fitting strength of the drive shaft 54, the length of the inner race 51c in the drive shaft axis direction is longer than the length of the outer race 51b in the drive shaft axis direction.

  A large number of balls 51d corresponding to rolling elements are disposed between the inner race 51c and the outer race 51b in a state in which the relative movement of the inner race 51c and the outer race 51b in the drive shaft axis direction can be restricted.

  Thus, the bearing 51 is positioned by restricting the movement of the outer race 51b in the direction of the drive shaft, and the drive shaft 54 is press-fitted and fixed to the inner race 51c. The movement in the direction can be restricted (that is, the drive shaft 54 is prevented from coming off).

  On the other hand, the bearing 52 disposed in the third center hole 72c of the third cylinder 71c has a cylindrical outer race 52b fitted into the stepped third center hole 72c. And the end surface of the outer race 52b in the drive shaft axis direction faces the end surface of the stepped portion of the third center hole 72c and the end surface of the fourth cylinder 71d on the third cylinder 71c side.

  A drive shaft 54 is loosely fitted into the cylindrical inner race 52c. For this reason, the bearing 52 can be easily assembled to the drive shaft 54. The length of the inner race 52c in the drive axis direction is equal to the length of the outer race 52b in the drive axis direction.

  A large number of balls 52d corresponding to rolling elements are disposed between the inner race 52c and the outer race 52b in a state in which the relative movement of the inner race 52c and the outer race 52b in the drive shaft axis direction can be restricted.

  Further, both the bearing 51 and the bearing 52 are provided with seal plates 51a and 52a. With respect to the bearing 51, the seal plate 51a is located on the front end side of the drive shaft 54, and with respect to the bearing 52, the seal plate 52a is the fourth cylinder. The arrangement is directed to the 71d side.

  3 is a view showing only the third cylinder 71c, FIG. 3 (a) is a perspective view of the third cylinder 71c, and FIG. 3 (b) is a front view of the third cylinder 71c (the axial direction of the pump device 100). Figure seen from). However, in FIG. 3, the illustration of a groove in which an O-ring 74 c described later is disposed is omitted.

  As shown in this figure, the third center hole 72c has a portion having an inner diameter equivalent to the outer diameter of the bearing 52 and a portion reduced than the inner diameter of the bearing 52, whereby the stepped portion is formed. It is configured. When the bearing 52 is pushed to the stepped portion, the bearing 52 enters the inside of the third center hole 72c, and a cavity remains on the fourth cylinder 71d side in the third center hole 72c. A part of the fourth cylinder 71d enters the cavity.

  And the drive shaft 54 is inserted in the 1st-4th center holes 72a-72d equivalent to a shaft insertion hole, and is supported by the bearings 51 and 52. As shown in FIG. As described above, the bearings 51 and 52 are arranged on both sides of the rotary pumps 10 and 13.

  Note that a suction port 62, which will be described later, is also configured by the third cylinder 71c. The configuration of the suction port 62 will be described later in detail.

  4 is a cross-sectional view taken along line AA in FIG. Hereinafter, the configuration of the rotary pumps 10 and 13 will be described with reference to FIGS. 2 and 4.

  The rotary pump 10 is disposed in a rotor chamber 50a formed by sandwiching both sides of a cylindrical first central plate 73a between a first cylinder 71a and a second cylinder 71b, and is driven by a drive shaft 54. It consists of a tangential gear pump (trochoid pump).

  Specifically, the rotary pump 10 includes a rotating portion including an outer rotor 10a having an inner tooth portion formed on the inner periphery and an inner rotor 10b having an outer tooth portion formed on the outer periphery, and the inner rotor 10b. The drive shaft 54 is inserted into the hole. A key 54b is inserted into a long hole 54a (see FIG. 2) formed in the drive shaft 54, and torque transmission to the inner rotor 10b is performed by the key 54b.

  The outer rotor 10a and the inner rotor 10b have a plurality of gaps 10c formed by meshing inner teeth and outer teeth formed respectively. Then, the suction and discharge of the brake fluid is performed by changing the size of the gap 10 c by the rotation of the drive shaft 54.

  On the other hand, the rotary pump 13 is disposed in a pump chamber 50b formed by sandwiching both sides of a cylindrical second central plate 73b between the second cylinder 71b and the third cylinder 71c. Similarly to the rotary pump 10, the rotary pump 13 is also composed of an internal gear pump having an outer rotor 13a and an inner rotor 13b, and is arranged by rotating the rotary pump 10 by 180 ° around the drive shaft 54. It has become. By arranging in this way, the suction-side gap 10c and the discharge-side gap 10c of each of the rotary pumps 10 and 13 are symmetric with respect to the drive shaft 54, so that the high-pressure on the discharge side is high. The force applied to the drive shaft 54 by the brake fluid pressure can be offset.

  The first cylinder 71 a is formed with a suction port 60 that communicates with the suction-side gap 10 c of the rotary pump 10. The suction port 60 is formed so as to penetrate from the end surface on the rotary pump 10 side of the first cylinder 71a to the end surface on the opposite side. For this reason, the brake fluid is introduced with the end surface of the suction port 60 opposite to the end surface on the rotary pump 10 side as an inlet.

  The suction port 60 is connected to a suction conduit 151 formed so as to reach the bottom surface of the recess 150 a with respect to the housing 150.

  The second cylinder 71 b is provided with a discharge port 61 that communicates with the gap 10 c on the discharge side of the rotary pump 10. The discharge port 61 extends from the end surface on the rotary pump 10 side to the outer peripheral surface. Specifically, the discharge port 61 is configured as follows.

  An annular groove 61 a formed so as to surround the drive shaft 54 is provided on the end surface of the second cylinder 71 b on the rotary pump 10 side.

  A ring-shaped seal member 171 is provided in the annular groove 61a. The seal member 171 includes a resin member 171a disposed on the rotary pump 10 side and a rubber member 171b that presses the resin member 171a toward the rotary pump 10 side. The seal member 171 is disposed on the inner peripheral side so that a gap between the outer plate 10a on the suction side and the outer periphery of the outer rotor 10a facing the suction portion 10c and the central plate 73a is located. On the outer peripheral side, the gap between the outer periphery of the outer rotor 10a facing the discharge-side gap 10c and the discharge-side gap 10c and the central plate 73a is located. That is, the seal member 171 is configured to seal the relatively low pressure portion and the relatively high pressure portion of the inner and outer circumferences of the seal member 171.

  Further, the seal member 171 is configured to be in contact with the inner periphery of the annular groove 61a and to be in contact with only a part of the outer periphery, and a portion of the annular groove 61a that is not partially in contact with the outer periphery side of the seal member 171 is There is a gap. That is, the annular groove 61a has a region configured so that the entire outer periphery does not come into contact with the seal member 171, and the brake fluid can flow in this region. Further, a pipe 61b is drawn from a part of the annular groove 61a to the second cylinder 71b. The discharge port 61 is configured by the gap between the annular groove 61a configured as described above and the pipeline 61b.

  The discharge port 61 is a discharge pipe formed in the housing 150 via an annular groove 162 formed in the entire circumference of the inner peripheral surface of the recess of the housing 150 where the tip position of the pump device 100 is disposed. It is connected to the path 152.

  In addition, a discharge port 63 communicating with the gap on the discharge side is provided on the end surface of the second cylinder 71b opposite to the end surface where the discharge port 61 is formed.

  The discharge port 63 is formed from the end surface of the second cylinder 71b to the outer peripheral surface. The discharge port 63 is formed in the same structure as the discharge port 61 described above, and the gap between the annular groove 63a that accommodates the ring-shaped seal member 172 including the resin member 172a and the rubber member 172b, and the annular groove 63a. It is comprised from the pipe line 63b pulled out from the uppermost position. The discharge port 63 is connected to the discharge conduit 154 via an annular groove 163 formed in the entire periphery of the inner peripheral surface of the recess 150a of the housing 150 facing the outer periphery of the center plate 73b.

  The third cylinder 71 c is provided with a suction port 62 that communicates with a suction side gap of the rotary pump 13.

  The suction port 62 is formed so as to penetrate from the end face on the rotary pump 13 side to the opposite end face of the third cylinder 71c and to the outer peripheral face of the third cylinder 71c on the opposite end face.

  Specifically, the suction port 62 is configured by utilizing a third center hole 72c formed in the third cylinder 71c, and is configured by expanding the diameter of the third center hole 72c to form a groove. ing. As shown in FIGS. 3A and 3B, the third center hole 72c of the third cylinder 71c has an oval shape on the rotary pump 13 side (the back side in the drawing). The drive shaft 54 is disposed near the semicircular shape of the upper end of the oval, and a gap constituting the suction port 62 is formed between the semicircle of the lower end and the drive shaft 54. Yes. In addition, about the shape of the 3rd center hole 72c here, although the lower edge part was made into circular arc shape, it is good also as rectangular shape.

  The third center hole 72c is expanded in diameter so as to have the same diameter as the bearing 52 at an intermediate position of the third cylinder 71c, and is long on the end surface of the third cylinder 71c opposite to the rotary pump 13 side. The circular lower end is connected to a groove reaching the outer peripheral surface of the third cylinder 71c. This groove is formed by, for example, a rectangular cross section or an oval semicircular shape, but in this embodiment, it is a rectangular cross section.

  The suction port 62 is a portion of the third central hole 72c that is not closed even when the bearing 52 is disposed, that is, a crescent-shaped portion, and an end surface of the third cylinder 71c opposite to the rotary pump 13 side. In FIG. 3, the groove extends to the outer peripheral surface of the third cylinder 71c. For this reason, the brake fluid is introduced with the outer peripheral surface side of the third cylinder 71c of the suction port 62 as the inlet. The suction port 62 is a suction pipe formed in the housing 150 via an annular groove 164 formed on the entire inner peripheral surface of the recess 150a of the housing 150 so as to include the position of the inlet of the suction port 62. It is connected to the path 153.

  In FIG. 2, a suction conduit 153 and a discharge conduit 154 correspond to the conduit C in FIG.

  As described above, by configuring the suction port 62 using the third center hole 72c, the brake fluid is supplied to the drive shaft 54, the bearing 52, and the like, so that the drive shaft 54 rotates smoothly. Further, since the suction port 62 is located closer to the motor 11 (outside the housing 150) than the discharge port 63, the brake fluid pressure in the portion near the outside of the housing 150 can be lowered.

  The second center hole 72b of the second cylinder 71b is partially made larger in diameter than the drive shaft 54, and the first rotary pump 10 and the second rotary pump 13 are placed in the enlarged part. A sealing member 80 is stored. The seal member 80 is obtained by fitting an O-ring 81, which is a ring-shaped elastic member, into a ring-shaped resin member 82 in which a groove portion having a radial direction as a depth direction is formed. The resin member 82 is pressed by force so as to come into contact with the drive shaft 54.

  Although not shown, for example, the cross-sectional shapes of the resin member 82 and the second center hole 72b of the second cylinder 71b are both circular arcs having a circular cutout, and the second cylinder 71b The resin member 82 is configured to be fitted into the center hole 72b. For this reason, the notch part of the resin member 82 plays a role as a key, and the seal member 80 is configured so as not to rotate relative to the second cylinder 71b.

  The fourth cylinder 71d is recessed on the surface opposite to the surface on which the disc spring 210 is disposed, and the drive shaft 54 is protruded from the recess. The drive shaft 54 is provided with a key-shaped connection portion 54c at the protruding end, and the drive shaft 11a of the motor 11 is inserted into the connection portion 54c. A single drive shaft 54 is rotated by the motor 11 via the drive shaft 11a, and the rotary pumps 10 and 13 are driven.

  The diameter of the inlet of the recessed portion of the fourth cylinder 71d is the same as the hole 11c formed in the holder 11b of the motor 11, and the recessed portion of the fourth cylinder 71d and the hole 11c of the holder 11b of the motor 11 The bearing 180 is arranged with a small gap between them, and the drive shaft 11a is pivotally supported. In this example, the drive shaft 11a is pivotally supported by the bearing 180, but the drive shaft 54 may be pivotally supported.

  Thus, when the bearing 180 is disposed in the hole 11c formed in the holder 11b of the motor 11 and the recessed portion of the fourth cylinder 71d, the motor 11 and the fourth cylinder 71 are positioned in the radial direction. Thus, the axial displacement between the 11 drive shafts 11a and the drive shaft 54 can be minimized.

  Further, a seal member 90 and an oil seal 91 are aligned and fixed in the axial direction of the drive shaft 54 so as to cover the outer periphery of the drive shaft 54 in a recess formed in the fourth cylinder 71d. The seal member 90 has the same configuration as the seal member 80 and serves to seal brake fluid leaking from the suction port 62.

  Furthermore, O-rings 74a, 74b, 74c, and 74d are disposed on the outer peripheral surfaces of the first to fourth cylinders 71a to 71d, respectively. These O-rings 74 a to 74 d seal the brake fluid in suction pipes 151, 153 and discharge pipes 152, 154 formed in the housing 150, and the suction pipe 151 and the discharge pipe 152. Between the discharge conduit 152 and the discharge conduit 154, between the discharge conduit 154 and the suction conduit 153, and between the suction conduit 153 and the outside of the housing 150.

  In addition, the outer peripheral surface of the front end on the inlet side of the recessed portion of the fourth cylinder 71d is reduced in diameter to form a stepped portion. The ring-shaped male screw member 200 described above is fitted into the reduced diameter portion, and the pump device 100 is fixed.

  Next, the operation of the brake device and the pump device 100 configured as described above will be described.

  The brake device is at the time of ABS control in which the wheel tends to be locked, or when a large braking force is required (for example, when the braking force corresponding to the brake pedal force cannot be obtained or the operation amount of the brake pedal 1 is large). , The pump device 100 is driven to suck the brake fluid in the reservoir 40, and the pressure is increased and discharged. Then, the pressure of the wheel cylinders 4 and 5 is increased by the discharged high-pressure brake fluid.

  At this time, in the pump device 100, the basic pump operation is such that the rotary pumps 10 and 13 suck the brake fluid through the suction pipes 151 and 153 and discharge the brake fluid through the discharge pipes 152 and 154. Do.

  At this time, in the rotary pumps 10 and 13, the pressure on the discharge side becomes very large. For this reason, the brake fluid pressure acts in a direction in which the pump device 100 is removed from the housing 150. As described above, the axial force of the pump device 100 is secured by the disc spring 210 and the male screw member 200. It is possible to prevent the 100 from rattling in the housing 150.

  In the case of this embodiment, on the motor 11 side with respect to the rotary pump 10, the cylinder parts constituting the outer shape of the pump device 100 are not constituted by one part, but two parts, a third cylinder 71c and a fourth cylinder 71d. The disc spring 210 is disposed between the third cylinder 71c and the fourth cylinder 71d.

  In the pump body provided in the conventional vehicle brake device, the cylinder part constituting the outer shape of the pump body is constituted by one part on the motor side of the rotary pump, and the suction port is formed in the cylinder part. Therefore, since the cylinder parts must be provided with bearings and seals, the length in the axial direction has to be large, but there is a space where nothing is arranged at the outer peripheral position than the bearings and seals. A dead space was formed.

  On the other hand, in this embodiment, since the disc spring 210 is arranged between the third cylinder 71c and the fourth cylinder 71d, the space can be effectively used. For this reason, compared with the case where the disc spring 210 is arrange | positioned in the front-end | tip position of the pump apparatus 100, the total axial direction length (pump shaft of the pump apparatus 100 including the 3rd cylinder 71c, the 4th cylinder 71d, and the disc spring 210 is included. (Length) can be shortened.

  In such a structure, the disc spring 210 is oriented such that the bottom side of the disc spring 210 (the side on which the outer peripheral portion is loaded) faces the rotary pumps 10 and 13 and the top side of the disc spring 210 (inner circumference). The side on which the load is applied to the part) faces the motor 11 side.

  If the disc spring 210 is configured such that the upper surface side of the disc spring 210 faces the rotary pumps 10 and 13 and the bottom surface side of the disc spring 210 faces the motor 11 side, the following problems occur. there's a possibility that.

  That is, for example, the reaction force when the pump device 100 is pressed against the bottom surface of the recess 150a causes the outer periphery of the first cylinder 71a, the first center plate 73a, the outer periphery of the second cylinder 71b, the second center plate 73b, and the third. When transmitted to the disc spring 210 side via the outer peripheral portion of the cylinder 71c, this load must be received on the upper surface side of the disc spring 210. In this case, since the position where the load is applied is on the outer peripheral side of the third cylinder 71c, the position where the load is received is on the inner peripheral side of the third cylinder 71c, so that the displacement of the third cylinder 71c is possible. There is sex.

  On the other hand, in this embodiment, the load can be received on the bottom surface side of the disc spring 210, that is, on the outer peripheral side of the third cylinder 71c. For this reason, the load can be reliably received on the bottom surface side of the disc spring 210, and the deformation of the third cylinder 71c can be prevented.

  Further, in the present embodiment, the bearing 51 is positioned by restricting the movement of the outer race 51b in the direction of the drive shaft, and the drive shaft 54 is press-fitted and fixed to the inner race 51c. Retaining can be performed. Therefore, a retaining member is not required, and the number of parts can be reduced and the drive shaft 54 can be shortened.

  Further, since the inner race 51c is longer than the outer race 51b, the press-fit strength of the drive shaft 54 can be secured while suppressing the increase in the size of the outer race 51b (that is, while suppressing the increase in the size of the pump device 100). The pump device 100 can be reduced in size while increasing the reliability of stopping.

  Further, since the outer race 51b is in contact with the end surface of the stepped portion of the first center hole 72a and the bottom surface of the recess 150a, the movement in the drive shaft axis direction is restricted. The movement of the drive shaft 54 can be restricted in both directions. Therefore, it is not necessary to provide the drive shaft 54 with a large-diameter portion as in the above-described conventional configuration, and the shape of the drive shaft 54 can be simplified.

  Further, since the outer race 51b is loosely fitted to the first cylinder 71a, the deformation of the first cylinder 71a due to the press-fitting of the outer race 51b can be prevented. Similarly, since the outer race 52b is loosely fitted to the third cylinder 71c, the deformation of the third cylinder 71c due to the press-fitting of the outer race 52b can be prevented.

  Further, in the bearing 52 that is not involved in preventing the drive shaft 54 from coming off, the drive shaft 54 is loosely fitted to the inner race 52c, so that the bearing 52 can be easily assembled to the drive shaft 54.

  Further, in the bearing 52 that is not involved in preventing the drive shaft 54 from coming off, the length of the inner race 52c in the drive shaft axis direction is made equal to the length of the outer race 52b in the drive shaft axis direction. Therefore, the pump device 100 can be reduced in size because the length of the inner race 52c in the direction of the drive shaft is shortened, and a general-purpose one can be adopted for the bearing 52, thereby suppressing an increase in cost. .

  In the present embodiment, the outer race 51b of the bearing 51 disposed in the first center hole 72a of the first cylinder 71a is brought into contact with the end surface of the stepped portion of the first center hole 72a and the bottom surface of the recess 150a. Thus, the movement in the drive shaft axis direction is restricted to prevent the drive shaft 54 from coming off. According to this, for example, the outer race 52b of the bearing 52 disposed in the third center hole 72c of the third cylinder 71c is brought into contact with the third cylinder 71c and the fourth cylinder 71d, thereby moving in the drive shaft axis direction. The movement range of the drive shaft 54 can be made smaller than when the drive shaft 54 is prevented from coming off by restricting the above.

  That is, the third cylinder 71c and the fourth cylinder 71d are relatively movable in the drive shaft axis direction, and depending on various factors such as the spring constant of the disc spring 210 and the tightening torque of the male screw member 200, Since the distance between the four cylinders 71d in the direction of the drive shaft axis is greatly varied, it is difficult to reduce the movement range of the outer race 52b in the direction of the drive shaft axis.

  On the other hand, in the bearing 51 disposed in the first center hole 72a of the first cylinder 71a, the movement range of the outer race 51b in the drive shaft axis direction is stepped in the first center hole 72a into which the outer race 51b is inserted. Since it is determined by the depth of the hole and the dimension in the drive shaft axis direction of the outer race 51b, the movement range of the outer race 52b in the drive axis direction can be easily reduced.

(Other embodiments)
In the above embodiment, ball bearings are used as the bearings 51 and 52 that support the drive shaft 54, but radial bearings (for example, cylindrical roller bearings and tapered roller bearings) other than ball bearings may be used.

  In the above embodiment, the outer race 51b is brought into contact with the end surface of the stepped portion of the first center hole 72a and the bottom surface of the recess 150a, thereby restricting the movement of the outer race 51b in the drive shaft axis direction. Not limited to this, the outer race 51b may be press-fitted into the first center hole 72a to restrict the movement of the outer race 51b in the drive shaft axis direction.

  In the above-described embodiment, the drive shaft 54 is loosely fitted to the inner race 52c of the bearing 52. However, the present invention is not limited to this, and the drive shaft 54 may be press-fitted and fixed to the inner race 52c of the bearing 52.

  Further, in order to suppress the deformation of the third cylinder 71c, it is desirable that the outer race 52b is disposed by clearance fit as in the above embodiment, but in the present invention, it is disposed by such clearance fit. The configuration is not essential. For example, the outer race 52b may be fixed to the third cylinder 71c by press-fitting. When the outer race 52b is fixed by press-fitting, it is possible to restrict the movement of the outer race 52b in the drive shaft axis direction.

In the above embodiment, the length of the inner race 52c of the bearing 52 in the direction of the drive shaft is equal to the length of the outer race 52b in the direction of the drive axis. The outer race 52b may be longer than the length in the drive shaft axis direction.

  Moreover, in the said embodiment, although the example which applied the pump apparatus of this invention to the brake device for vehicles was shown, the pump apparatus of this invention is applicable other than the brake device for vehicles.

It is a figure which shows the brake device for vehicles using the pump apparatus which concerns on one Embodiment of this invention. It is sectional drawing of the pump apparatus 100 containing the rotary pumps 10 and 13 of FIG. (A) is a perspective view of the 3rd cylinder 71c, (b) is a front view of the 3rd cylinder 71c. It is sectional drawing which follows the AA line of FIG.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10, 13 ... Pump, 51, 52 ... Bearing, 51b, 52b ... Outer race, 51c, 52c ... Inner race, 51d ... Ball (rolling element), 54 ... Drive shaft, 71a-71c ... Cylinder (first case), 71d ... Cylinder (second case), 150 ... Housing, 150a ... Recess, 210 ... Disc spring (spring means).

Claims (5)

A drive shaft (54) is inserted into the first case (71a-71c), and the drive shaft (54) is rotatably supported by bearings (51, 52), and the first case (71a-71c) A pump device for sucking and discharging fluid by driving the pump (10, 13) housed in the drive shaft (54),
The bearing (51) is disposed in an inner race (51c) in which the drive shaft (54) is press-fitted and fixed and in the first case (71a to 71c) in a state where movement in the direction of the drive shaft is restricted. Between the inner race (51c) and the outer race (51b) in a state in which the relative movement of the inner race (51b) and the inner race (51c) and the outer race (51b) in the drive shaft axis direction can be restricted. and a disposed a rolling element (51d), and the length Kuna' than the drive shaft axial length of the inner race (51c) of the drive shaft axial length the outer race (51b),
A second case (71d) disposed coaxially with the first case (71a-71c) and capable of moving relative to the first case (71a-71c) in the drive shaft axis direction; Spring means disposed between one case (71a to 71c) and the second case (71d) for biasing the first case (71a to 71c) and the second case (71d) away from each other (210)
The first case (71a to 71c) and the second case (71d) are inserted into the recess (150a) of the housing (150) with the first case (71a to 71c) side as a tip, and the recess (150a) The second case (71d) is pressed from the inlet side toward the first case (71a-71c) side and fixed.
The outer race (51b) is in contact with the end surface of the first case (71a to 71c) facing the bottom surface of the recess (150a) and the bottom surface of the recess (150a), and the movement in the drive shaft axis direction is restricted. The pump apparatus characterized by the above-mentioned.   The outer race (51b) is fitted in the first case (71a to 71c) and is contacted with the end surface of the first case (71a to 71c) in the drive shaft axial direction. The pump device according to claim 1, wherein the movement is restricted. The drive shaft (54) is rotatably supported by a plurality of bearings (51, 52),
Among the plurality of bearings (51, 52), some of the bearings (51) are in an inner race (51c) in which the drive shaft (54) is press-fitted and fixed, and movement in the drive shaft axis direction is restricted. The inner race (51b) disposed in the first case (71a to 71c), the inner race (51c) and the outer race (51b) in a state in which relative movement in the drive shaft axis direction can be restricted. (51c) and a rolling element (51d) disposed between the outer race (51b), and the inner race (51c) has a drive shaft axial length that is the drive shaft of the outer race (51b). Longer than the direction length,
The other bearing (52) of the plurality of bearings (51, 52) is characterized in that the length of the inner race (52c) in the drive shaft axial direction is equal to the length of the outer race (52b) in the drive shaft axial direction. Item 3. The pump device according to Item 1 or 2. The drive shaft (54) is rotatably supported by a plurality of bearings (51, 52),
Among the plurality of bearings (51, 52), some of the bearings (51) are in an inner race (51c) in which the drive shaft (54) is press-fitted and fixed, and movement in the drive shaft axis direction is restricted. The inner race (51b) disposed in the first case (71a to 71c), the inner race (51c) and the outer race (51b) in a state in which relative movement in the drive shaft axis direction can be restricted. (51c) and a rolling element (51d) disposed between the outer race (51b), and the inner race (51c) has a drive shaft axial length that is the drive shaft of the outer race (51b). Longer than the direction length,
The other bearing (52) of the plurality of bearings (51, 52) is characterized in that the drive shaft (54) is fitted in an inner race (52c). The pump apparatus as described in any one. The pumps (10, 13) are constituted by gear pumps housed in the first cases (71a to 71c), the bearings (51, 52) are constituted by ball bearings, and drive the gear pumps (10, 13). The pump device according to any one of claims 1 to 4, wherein a drive shaft (54) to be rotated is rotatably supported by the ball bearings (51, 52).

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