JP5347184B2 - pump - Google Patents

Abstract

The invention relates to a pump, especially a vane-cell vacuum pump, for motor vehicle servobrake systems, said pump comprising a rotor (7) which is rotatably driven by a drive by means of a wrap spring clutch (23).

Description

  The present invention relates to a pump, particularly a vane-type vacuum pump, used in a vehicle brake booster according to the preamble of claim 1.

  A pump of the type described in the present invention is known (Patent Document 1). Such a pump plays a role of applying a negative pressure to a braking force booster of a vehicle and has a rotor that is rotated by a driving device. The coupling between the rotor and the drive device is performed via a clutch having a coil spring that is wound around to transmit drive torque when the pump of the drive device rotates in the rotational direction. When the drive device rotates in the direction opposite to the rotation direction of the pump, the coil spring can slip through. Such a clutch ensures that the rotor is not driven in the wrong direction when the drive device inadvertently runs backward. This coil spring can also be designed so that if the clutch exceeds a desired maximum torque, it slips out and does not overload the rotor. The pump is always driven while the vehicle is running, resulting in an increase in energy consumption and an increase in the amount of harmful substances emitted in the internal combustion engine.

European Patent Application Publication No. 1277960

  An object of the present invention is to manufacture a pump that does not include such disadvantages.

  In order to solve this problem, a pump including the technical features recited in claim 1 has been proposed. This pump has a rotor that is rotated by a drive device via a coil spring clutch, for example, for the purpose of generating negative pressure in a braking force booster of a vehicle. This coil spring acts together with the rotor of the pump, and the torque of the driving device is transmitted to the rotor by fixing the coil spring to the rotor and the shaft journal of the driving device. This pump has a clutch device that extends the coil spring to the operating position, thereby ensuring that the coil spring is in close contact with the shaft journal and / or the rotor and that no further torque is transmitted from the drive device. To do.

  In another operating position, the clutch does not prevent the coil springs from contracting, thereby providing a coupling between the rotor and the drive and driving the drive.

  Such an embodiment has the advantage that the clutch can be disengaged when the pump reaches a desired negative pressure within the vehicle brake force booster. There is no further burden on the drive, and as a result no unnecessary energy burden is generated.

  Preferred is a pump in which the clutch device includes a clutch member. The clutch member is movable in the direction of the longitudinal axis of the coil spring and acts with the first end of the spring. The clutch member has a clutch surface that is inclined at a constant angle with respect to the longitudinal axis of the coil spring, so that the clutch member moves in the direction of the longitudinal axis of the coil spring. As a result of the rotation of one end, in particular the spring, in the direction opposite to the drive direction of the shaft journal, the clutch member moves towards an operating position where the inner diameter of the spring increases. As a result, transmission of the torque of the shaft journal to the rotor is prevented. That is, the pump clutch is disengaged.

  In another preferable pump, it is considered that the clutch member is designed as a clutch sleeve provided concentrically with the longitudinal axis of the coil spring. Such a design is characterized by a particularly compact configuration.

  In another preferable pump, it is considered that the clutch member of the clutch device is operated by hydraulic pressure. This makes it possible to implement the clutch device with a simple configuration at low cost.

  Another pump is preferable in that the clutch device has an elastic member. This elastic member pushes the clutch member to the operating position where the coil spring is connected to the rotor. This configuration is particularly easy and therefore is less prone to failure.

  In another preferred pump, it is considered that the clutch device is switched depending on the pressure in the braking force booster of the vehicle. This pump therefore stops operating whenever a sufficient pressure, in particular a negative pressure, is generated.

  In another preferred pump, there is provided an oil supply device that is shut off when the drive of the pump rotor is shut off.

  In another preferred pump, it is taken into account that the clutch sleeve forms a pressure chamber with the housing around the rotor. This achieves a particularly compact configuration of the pump.

  Other embodiments of the pump are indicated in the dependent claims.

  The invention will be described in more detail on the basis of the accompanying drawings.

It is the schematic sectional drawing which showed 1st Embodiment of the pump which has a clutch apparatus in the cross section of the longitudinal direction. It is an expansion perspective view of the clutch member of a clutch apparatus. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. FIG. 2 shows various embodiments of a pump having a clutch device. It is a side view of the edge part of a coil spring.

  From the schematic diagram of FIG. 1, the first of the pump (1) having a housing (3) containing a pump chamber (5) containing a vane (not shown) of a vane-type pump which can be driven in rotation by a rotor (7). The embodiment is clear. The pump is used to generate a negative pressure in a vehicle brake force booster. Oil to be used for lubricating the pump (1) can be supplied to the pump from the oil pump (9) through the pipe (11) and the hole (13) provided in the housing (3). Is possible. In the following, this point will be discussed in more detail.

  The rotor (7) is supported by a bearing protrusion (17) provided concentrically with the rotor and its rotating shaft (15). The hole (13) in the housing (3) opens at the contact portion between the bearing protrusion (17) and the rotor (7), thereby ensuring lubrication of the rotor (7).

  The rotor (7) has a small outer diameter at the end opposite the pump chamber (5) and protruding from the bearing protrusion (17) compared to the rest of the rotor (7) and A cylindrical protrusion (19) configured to contact the coil spring (21) of the coil spring clutch (23) is provided. The inner diameter of the coil spring (21) substantially coincides with the outer diameter of the protrusion (19), and when the coil spring (21) is relaxed, the coil spring (21) and the protrusion (19) The frictional force acting between the two is small.

  When the length of the coil spring (21) is measured in the direction of the rotating shaft (15), the length of the coil spring (21) protrudes beyond the length of the protrusion (19), and the details of the drive device not shown in detail in the present invention. The shaft journal (25) is selected to be accommodated. The outer diameter of the shaft journal coincides with the outer diameter of the protrusion (19), whereby the outer surfaces of the protrusion (19) and the shaft journal (25) are aligned with each other. )

  The shaft journal (25) includes an extension (27) that engages with a recess (29) provided from the right side of the rotor (7) to the protrusion (19). The outer diameter of the extension (27) is adjusted in accordance with the inner diameter of the recess (29). As a result, the extension (27) is supported inside the recess (29) so as to be rotatable with less friction. become. The extension part (27) is configured in a shape suitable for the purpose of holding the extension part (27) so that it does not slip out in the axial direction. For example, here, a retaining ring (31) that engages with a groove (33) provided on the inner surface of the recess (29) on one side and a groove (35) provided on the inner surface of the extension (27) is provided on the other side. .

  The shaft journal (25) of the drive device is fixed to the shaft journal (25) and the protrusion (19) in this case when rotation is applied in the first direction, in particular in the direction of operation of the pump (1). A frictional force acts on the coil spring (21) that is wound so as to be pulled. As a result, the torque of the drive device, that is, the shaft journal (25) is transmitted to the protrusion (19) and further to the rotor (7), so that, for example, rotation is given to the vanes in the pump chamber (5) and negative A pressure is formed.

  The coil spring clutch (23) is designed as follows. When the shaft journal (25) rotates in the opposite direction, the coil spring (21) extends and relaxes due to the frictional force between the outer surface of the shaft journal (25) and the inner surface of the coil spring (21), thereby the coil spring. The inner diameter of (21) expands at least in the portion of the shaft journal (25). As a result, torque is further transmitted to the coil spring (21) and the protrusion (19) of the rotor (7) by the shaft journal (25). It becomes impossible.

  The pump (1) is in a state where the driving device is operating, that is, in a state where the shaft journal (25) is rotated in the driving direction in which the coil spring (21) is fixed and pulled. A clutch device (37) used for disengaging the clutch of (1) is provided. When the pump (1) is used in a vehicle, the coil spring (21), in particular, contracts against the shaft journal (25) and is fixed to the outer surface of the shaft journal (25) by an engine, in particular an internal combustion engine. This pump (1) is driven so as to be given a rotation in the direction of being pulled in the wet state. At the same time, the coil spring (21) is in contact with the outer surface of the projecting portion (19). Accordingly, the projecting portion (19) is rotated from the drive device via the coil spring (21). Is given. In order to actuate the coil spring clutch (23) so that no torque is transmitted to the rotor (7) despite the rotation of the shaft journal (25), the clutch device (37) here has a rotating shaft. The clutch member is provided coaxially with (15) and formed as a clutch sleeve (39) that overlaps the rotor (7), the coil spring (21), and the shaft journal (25). The length of the clutch sleeve (39) is shown here only for the shaft journal (25), and is selected so that it barely overlaps a portion of the drive unit not shown in the present invention.

  On the other hand, the clutch sleeve (39) has an annular bead whose left end (41) protrudes into the bearing protrusion (17) of the housing (3) and is further away from the outer rotary shaft (15). According to (43), the length of the clutch sleeve (39) is selected so as to be in close contact with the inner surface (45) of the bearing protrusion (17). The front surface (47) of the bearing protrusion (17) is sealed by a seal plate (49) that is in close contact with the peripheral surface (53) of the clutch sleeve (39) by the inner edge portion (51). Between the seal plate (49) and the annular bead (43) of the clutch sleeve (39), and further inside the bearing projection (17) is in the housing (3), here the bearing projection (17). A sealed chamber (55) is provided through the hole (57) provided therein so as to prevent leakage in a state of communication with the pipe (59). The seal plate (49) can also be made of metal. The left end (41) of the clutch sleeve (39) is provided with an elastic member, here formed as a coil spring (61), which is on the one hand the rotor (7) and on the other hand the clutch sleeve (39). A preload is applied to the clutch sleeve (39), which is supported by the left end (41) of the left and right ends. The clutch sleeve (39) rotates together with the rotor (7) when the rotor (7) is driven. This point also applies to the coil spring (61).

  The clutch sleeve (39) is configured to be movable on the rotor (7) toward the coil spring (21) when viewed in the axial direction, that is, in the direction of the rotating shaft (15). As described in more detail below, when a working fluid, preferably oil, is introduced into the chamber (55) via piping (59) and holes (57) under pressure, the clutch sleeve of the chamber (55) When (39) exceeds a certain pressure, the coil spring (61) moves toward the first operating position on the left side against the force of the coil spring (61). In FIG. 1, the operating position of the clutch sleeve (39) in which the clutch sleeve (39) moves to the left against the force of the coil spring (61) beyond at least a certain range is reproduced. When the clutch sleeve (39) further moves to the left, the clutch sleeve (39) finally reaches the first operating position. In this first operating position, the coil spring (21) extends so as not to be pressed against the outer surface of the shaft journal (25) at least further. This point will be discussed in more detail below.

  When the chamber (55) is in a non-pressure state or when a pressure is applied to the clutch sleeve (39) to apply a force toward the left side that is smaller than the preload of the coil spring (61), the clutch sleeve (39) moves to the right side by the coil spring (61) until the annular bead (43) finally comes into contact with the inside of the seal plate (49). Therefore, this seal plate (49) serves as an element that restricts the passage of the clutch sleeve (39) to the right. When the clutch sleeve (39) is not in contact with the seal plate (49), the second operating position is taken. That is, the clutch sleeve (39) does not affect the coil spring (21). When the clutch sleeve (39) moves to the right side, the oil existing in the chamber (55) is pushed out of the chamber through the hole (57) and the pipe (59), and stored in, for example, a tank. Is done.

  FIG. 1 further shows that the clutch sleeve (39) includes a clutch surface (63), which acts with the first end (65) of the coil spring (21), the first The end portion is directed radially outward on the other peripheral surface of the coil spring (21), that is, in a direction away from the rotating shaft (15). A clutch surface (63) is a part of 1st recessed part (67) provided in the wall part (69) of a clutch sleeve (39).

  The coil spring (21) includes a second end (71) provided in the second recess (73) of the wall (69) of the clutch sleeve (39), and the second end (71) is a rotating shaft. Projecting toward the radially outer side on the peripheral surface of the coil spring with respect to (15).

  When measured in the direction of the rotating shaft (15), when the clutch sleeve (39) has reached the second operating position, it faces the left end (41) of one or both of the recesses (67) and (73). It is possible to select the lengths of the recesses (67) and (73) so that the wall surface of the boundary part comes into contact with the end of the coil spring (21) protruding into the recess. Therefore, contact with the clutch sleeve (39) can also be realized in this way.

  FIG. 2 is an enlarged perspective view of the clutch sleeve (39) of the clutch device (37). In this illustration, the left end portion (41) of the clutch sleeve (39) is disposed on the front surface. What can be clearly seen here is the annular bead (43) and the circumferential surface (53) of the clutch sleeve in contact with the annular bead (43). ) Is formed at the bottom of the groove (75). A first recess (67) including a clutch surface (63) is provided in the wall (69) at a certain distance from the left end (41). A first end (65) of a coil spring (21) not shown in FIG. 2 is engaged with the recess.

  The center of the clutch sleeve (39) coincident with the rotating shaft (15) shown in FIG. 1 at a suitable position in the wall (69), here, at a position substantially opposite in diameter to the first recess (67). A second recess (73) formed as a slit extending in parallel with the axis is provided. A second end (71) of a coil spring (21) (not shown here) is engaged with the slit.

  From the above description regarding the recesses (67) and (73) provided in the wall (69) of the clutch sleeve (39), the following becomes clear. That is, when the clutch sleeve (39) moves coaxially with the rotor (7) and further along with the rotation shaft (15), the second end portion (71) of the coil spring (21) is connected to the clutch sleeve (39). It is possible to slide along the surface of the second recess (73) without moving in the circumferential direction.

  When the clutch sleeve (39) moves to the left in the chamber (55) under pressure according to the example shown in FIG. 1, the clutch surface (63) inclined at a certain angle with respect to the rotating shaft (15) is splined. It acts on the first end (65) of the coil spring (21) in much the same way as the gear. When the clutch surface (63) moves to the left side of FIG. 1, the first end (65) of the coil spring (21) is twisted to the right, that is, clockwise when viewed from the observation direction of FIG. It becomes clear that it acts on the 1st end part (65) of this coil spring (21). During the above movement of the clutch sleeve (39) of the first end (65) of the coil spring (21), the rotation is performed so that the inner diameter of the coil spring is expanded at least to the shaft journal (25) of the drive device. By tilting the clutch surface (63) to the extent possible, it becomes impossible for the drive device to transmit any more torque to the coil spring (21) and further to the rotor (7).

  When the coil spring (21) is wound in the opposite direction, the clutch surface (63) needs to be inclined so as to be axisymmetric with respect to that shown in FIG.

  As seen in the circumferential direction of the clutch sleeve (39), it is clear that the second recess (73) plays a role of holding the second end (67) exclusively. In principle, it is also possible to hold the second end (71) in other ways without using this second recess.

  In the portion corresponding to the second recess (73), the second end (71) of the coil spring (21) is moved to the left side in the circumferential direction of the clutch sleeve (21) as the clutch sleeve (39) moves. It is conceivable to provide a clutch surface that is inclined so that it extends and moves to at least the rotor (7).

  As a whole, the first recess is assumed to extend substantially parallel to the rotating shaft (15), but it is also possible that a clutch surface of the type described here can be provided only in the second recess portion. It becomes. By forming these recesses in a shape suitable for the purpose, the inner diameter of the coil spring (21) is expanded to at least the portion of the shaft journal (25) when the clutch sleeve (39) is actuated. It is ensured that the coupling with the pump (1) is released. The clutch sleeve (39) shown in FIG. 1 is present due to the presence of differently preloaded portions in the contact surface of the coil spring (21) with the rotor (7) and the shaft journal (25). When the is operated and moved to the left side, a predetermined portion for removing the coil spring (21) can be provided.

  As long as the coil sleeve (61) allows the clutch sleeve (39) to apply no pressure or only a slight pressure in the chamber (55), the operating position, in particular the drive device, can be passed through the shaft journal (25). A situation is ensured that is coupled to the protrusion (19) of the rotor (7) and pushed to the second operating position where the pump (1) is driven.

  The clutch device (37) is preferably controlled by the pressure generated by the pump (1), here the negative pressure in the brake booster of the vehicle. This negative pressure is measured by a measuring pipe (77) communicating with the working side of the pump (1), that is, the negative pressure side. This negative pressure acts on the valve device (79) including a 4 / 2-way valve that forms a part of the clutch device (37). This 4 / 2-way valve takes various clutch positions depending on the pressure measured by the measuring tube (77).

  When a sufficient negative pressure is confirmed, the control piston of the 4 / 2-way valve moves to the position shown in FIG. As a result, the oil pump (9) communicates with the pipe (59), the hole (57) and the chamber (55), and preferably a working fluid as hydraulic working oil is supplied into the chamber (55). As a result of such pressurization, the clutch sleeve (39) moves to the first operating position described with reference to FIG. 1, and in this first operating position, the clutch surface (63) is the first of the coil spring (21). Engaging with the end (65), the first end (65) moves so that the inner diameter of the coil spring (21) expands to the portion of the shaft journal (25). From the example shown in FIG. 1, the first end (65) of the coil spring (21) has not yet reached the end of the first recess (67) facing the left end (41). it is obvious. The clutch sleeve (39) can move further to the left as compared to FIG. 1 in order to ensure the reliable release of the connection between the drive device and the rotor (7).

  From FIG. 1 it is clear that in the above-mentioned operating position of the 4/2 way valve, the hole (13) provided in the housing (3) is in a non-pressure state and preferably communicates with the tank (80). is there. Therefore, the supply of oil to the pump (1) performed via the oil pump (9) is interrupted. When the pressure obtained by the pump (1) falls below the desired value, this state is confirmed via the measuring tube (77) and controlled via the valve device (79). The control piston of the 4 / 2-way valve moves to the left compared to the position shown in FIG. Thereby, the oil pump (9) communicates with the hole (13) so as to ensure the oil supply to the pump (1). At the same time, the chamber (55) communicates with the tank (80) through the hole (57) and the pipe (59). This causes a pressure drop inside the chamber (55). Here, the coil spring (61) moves the clutch sleeve (39) to the right until the annular bead (43) contacts the inside of the seal plate (49) and the clutch sleeve (39) takes the second operating position. It can be moved. In this second operating position, the clutch surface (63) no longer acts on the first end (65) of the coil spring (21), so that the inner surface of the coil spring (21) and the shaft journal The coil spring (21) can be fixed to both the shaft journal (25) and the protrusion (19) of the rotor (7) by the frictional force acting between the outer surface of (25). The pump (1) is again connected to the drive.

  Overall, it is clear that the other parts of the coil spring clutch (23) can be switched in a simple manner. The drive device of the pump (1) moves the torque of the shaft journal (25) to the protrusion (19) of the rotor (7) with the coil spring (21) in a relaxed position relative to the coil spring (21). It is possible to release the connection depending on the pressure so that the action occurs in such a way that it will not be performed.

  The switchable coupling arrangement is simple and can be implemented more inexpensively.

  FIG. 3 shows another embodiment of a pump with a coil spring clutch in longitudinal section. The same members are denoted by the same reference numerals, and to the extent that this is the case, reference is made to the drawings described above.

  In the embodiment of the pump (1) described in FIG. 3, the housing is omitted. This pump (1) has a rotor (7) provided on the right side in FIG. 3 and rotated by a drive device not shown here. The torque of the drive device is introduced into a clutch bell (81) supported by at least one bearing (83). The right end portion (85) of the rotor is disposed, for example, in a pump chamber not shown here, and can accommodate a vane for supplying a working fluid, while the left end portion (87) of the rotor (7) This end is designed to engage the interior of the clutch bell (81). The rotor (7) is formed in a hollow shape, so that this rotor (7) can at least partially accommodate the coil spring clutch (23). The coil spring clutch (23) has a coil spring (21) whose left side portion is provided inside the clutch bell (81) and whose right side portion is housed inside the rotor (7). The clutch bell (81) includes an accommodating portion (89), and the left portion of the coil spring (21) is disposed in the accommodating portion, and the inner diameter thereof is on the inner surface when the coil spring (21) is unloaded. The size is selected so as not to come into contact. On the other hand, as described in more detail below, when the coil spring (21) is extended, the coil spring (21) comes into contact with the inner surface of the housing portion (89) by its peripheral surface, and as a result, the housing portion (89). The inner surface functions as a clutch surface.

  The coil spring clutch (23) includes a clutch device (37) having a positioning body (91) including a plurality of recesses on its peripheral surface, similar to the clutch sleeve (39) described with reference to FIGS. It is out. Here, the first recess (67) extending in the direction of the rotating shaft (15) and the clutch bell (81) of the rotor (7) and engaging with the first end (65) of the coil spring (21) is provided. Is recognized.

  The clutch body (91) includes, on its peripheral surface, a second recess that engages with the second end of the coil spring (21) that will be discussed with reference to FIG.

  Here, the clutch body (91) is composed of two parts, and the two parts (91a) and (91b) of the clutch body (91) connected using the screws (93) are in opposite directions. Can be rotated. The first part (91a) of the clutch body (91) acts on the first end (65) of the coil spring (21), and the second part (91b) is the second end of the coil spring (21). Therefore, the relative rotation of these two parts (91a) and (91b) makes it possible to adjust the predetermined spring preload during assembly of the coil spring clutch (23). The two parts (91a) and (91b) are fixed with screws (93) in the desired relative rotational position.

  The inner space (95) of the rotor (7) formed in a hollow shape is hermetically sealed by a closing member (97) on the pump chamber (5) side. The clutch body (91) is also formed in a hollow shape. Inside the hollow space (99) there is preferably a preloaded elastic member, here one on the closing member (97) and the other on the inner wall (103) of the clutch body (91). A supported coil spring (101) is provided. When the clutch body (91) is composed of two parts, the inner wall (103) is a part of the first part (91a) of the clutch body (91).

  The clutch body (91) can reciprocate in the direction of the rotation axis (15) in the internal space (95). In the illustrated example of FIG. 3, the clutch body (91) is moved to the first operating position, that is, the clutch body (91) is moved to the rightmost position from here, and the clutch body (91) is closed. It is located in the 1st operation position which contacts member (97). Instead of the closing member, it is also possible to provide another stopper for the clutch body (91). The coil spring (21) is fixed in the axial direction, that is, the axial direction when viewed in the direction of the central axis (15), whereby the first end (65) of the clutch body (91) is moved. At the same time, it is guided inside the first recess (67). Since the first recess (67) extends in parallel with the rotation shaft (15), the first end (65) receives a force acting in the circumferential direction when the clutch body (91) moves. There is no change in the spring preload through this first end (65) since there is nothing.

  The clutch body (91) is provided with a clutch flange (105) at the right end thereof, and the clutch flange (105) is in close contact with the inner surface of the internal space (95) of the rotor (7). The left part of the clutch body (91) adjacent to the clutch flange (105) has a smaller outer diameter and is in close contact with a part of the internal space (95) of the rotor (7). This forms a chamber (55) that can be filled with pressurized working fluid, preferably hydraulic fluid. Thus, in FIG. 3, when the pressure is selected as having a magnitude that exceeds the force of the coil spring (101) due to the force acting on the clutch flange (105) from the left side, Thus, the clutch body (91) can move to the position shown on the right side of FIG. 3 against the force of the coil spring (101). When the pressure inside the chamber (105) decreases to a value determined by the force of the coil spring (101), the clutch body (91) is pushed back to the left from the position shown in FIG. 3 by the coil spring (101). At this time, the first end (65) of the coil spring (21) remains inside the first recess (67). Similarly, since the coil spring (21) extends in the direction of the rotating shaft (15), the coil spring (21) does not receive a change in preload.

  When the clutch body (91) moves from the position shown in FIG. 3 to the left side by the force of the coil spring (101), the clutch bell (81) moves to the left end of the clutch body (91), that is, the second end here. The part (91b) is provided with a gap (107) whose inner diameter is selected so that at least a part of the part (91b) is accommodated by the gap (107).

  The outer diameter of the clutch body (91) is selected so that the clutch body (91) can freely move in the direction of the rotating shaft (15) within the coil spring (21). Therefore, the left part of the coil spring (21) is located between the left part (91b) of the clutch body (91) and the inner surface of the accommodating part (89) of the clutch bell (81).

  The inner space of the clutch bell (81) and the rotor so that the rotor (7) is rotatably supported with the clutch body (91) and the coil spring (21) of the coil spring clutch (23) inside the clutch bell (81). The outer diameter of (7) is adjusted according to each other. The left end (87) of the rotor (7) is supported by another bearing (109) provided on the inner surface of the clutch bell (81). The relative rotation of the clutch bell (81) and the rotor (7) is affected by the coil spring (21) of the coil spring clutch (23). That is, when the coil spring (21) provided on the circumferential surface of the clutch body (91) is extended by the operation of the clutch body (91), the circumferential surface of the coil spring (21) is moved to the accommodating portion (89 of the clutch bell (81). ), And the torque of the clutch bell (81) is transmitted to the rotor (7). At this time, the coil spring (21) is connected to the clutch body (91) so that the force introduced into the accommodating portion (89) rotates via the first end portion (65) together with the rotor (7). To communicate. Since the coil spring (21) is in frictional contact with the housing portion (89), the torque that has reached the peak value causes the clutch bell (81) to rotate relative to the coil spring (21) in this case. Is not transmitted to the rotor (7). Thereby, damage to the pump (1) is avoided. This aspect applies to all embodiments described herein.

  In a state where the coil spring (21) is extended, the coil spring (21) comes into contact with the inner surface of the clutch body (91). Thus, the coil spring (21) is further removed from the housing portion (89). ) Is not transmitted.

  FIG. 4 shows a perspective view of the clutch body (91) described based on FIG. The same symbols are assigned to the same members.

  That is, the clutch body (91) is composed of two parts, and includes a first part (91a) and a second part (91b). The first part is provided with a first recess (67) extending in the direction of the longitudinal axis of the clutch body (91) coinciding with the rotational axis (15) of the rotor (7) on the peripheral surface thereof. A clutch flange (105) having a larger outer diameter than the other part (91a) is provided.

  The peripheral surface of the second component (91b) extends at a constant angle with respect to the rotation axis (15) and functions to accommodate a second end of a coil spring (21) not shown here. A second recess (73) is provided.

  As described with reference to FIG. 3, the clutch body (91) is located at least partially inside the coil spring (21) not shown here.

  While the coil spring (21) is fixed in the axial direction, when the clutch body (91) moves in the direction of the rotating shaft (15), the second end in the first recess (67) of the first end (65). The relative movement of the coil spring (21) relative to the part (91b) occurs. At this time, when viewed in the circumferential direction of the clutch body (91), it becomes clear that no movement of the end portion occurs. On the contrary, the second end of the coil spring (21) located in the second recess (73) moves in the circumferential direction when the clutch body (91) moves. Thereby, depending on the moving direction of the clutch body (91), the degree of extension of the coil spring (21) is increased or decreased, so that the outer diameter of the coil spring (21) corresponds to this. Change, that is, enlarge or reduce.

  Since such a method of operation has already been described in connection with the clutch sleeve (39) on the basis of FIGS. 1 and 2, it is not necessary here to go into further detail in this regard. Moreover, while providing the 2nd recessed part (73) in parallel with respect to a rotating shaft (15), it is possible for the 1st recessed part (67) to extend at a fixed angle with respect to a rotating shaft (15). It becomes clear. Further, when the clutch body (91) moves in the axial direction with respect to the fixed coil spring (21), as long as the preload on the coil spring (21) increases or decreases, the recess (67) It is also possible to provide both (73) and (73) parallel to the rotation axis (15).

  Further, from FIG. 4, the first part (91a) and the second part (91b) of the clutch body (91) penetrate both the first part (91a) and the second part (91b) in the axial direction. It is derived that they are connected by a screw (93).

  The ends of the coil springs (21) engaged with the recesses (67) and (73) are each provided with a slide body in order to reduce the frictional force between the spring ends and the recesses. It is possible. This ensures an easily performed operation and minimizes wear.

  The following points are apparent from FIGS. 3 and 4.

  Here, the clutch body (91) is formed as a hydraulic piston. When the chamber (55) is filled with, for example, hydraulic fluid supplied from a rotor bearing, the clutch body (91) slides to the right in FIG. 3 against the force of the coil spring (101). The recesses (67) and (73) provided on the peripheral surface of the positioning body are formed on the outside of the coil spring (21) by the extension of the coil spring (21) during the movement of the clutch body (91). The diameter is reduced and the direction is determined. Thus, the coil spring (21) is in contact with the circumferential surface of the clutch body (91) and is separated from the inner surface of the housing portion (89) that acts as the clutch surface. As a result, torque is no longer transmitted from the clutch bell (81) to the coil spring. The clutch bell (81) can now freely rotate relative to the rotor (7). Thereby, the clutch of the pump (1) is disengaged.

  FIG. 5 shows an embodiment with a change of the pump (1) in a longitudinal section, and in this illustrated example, the pump housing is not shown. The same members are given the same reference numerals. To this extent, reference is made to the description of the above-mentioned specification regarding each figure.

  What can be seen from the figure is the clutch bell (81) and the rotor (7) partially engaged with the clutch bell (81), and the right end (85) of the rotor (7) is A vane is accommodated in this, and it forms so that a vane pump may be implemented. The left end portion (87) at the facing position is located inside the clutch bell (81). This clutch bell (81) also accommodates the coil spring (21) of the coil spring clutch (23) in this embodiment. The pump (1) of the present embodiment also includes a clutch device (37) that plays a role of enabling the clutch of the pump to be disengaged when necessary. The clutch device (37) is also composed of two parts in this embodiment, and includes a clutch body (91) including a sleeve-like first part (91a) and a sleeve-like second part (91b). ing. The two parts (91a) and (91b) are rotatable in opposite directions. These two parts (91a) and (91b) are fixed when viewed in the axial direction, ie in the direction of the rotation axis (15).

  The two parts (91a) and (91b) are provided on the circumferential surface of the clutch piston (91c), which here includes two components (91'c) and (91''c). The components (91'c) and (91 "c) are connected to each other by a screw (93) oriented in the direction coaxial with the rotation shaft (15).

  At least a part of the clutch piston (91c) is formed in a hollow shape, and accommodates an elastic member formed as a coil spring (101) here. In the embodiment shown here, only the component (91'c) is formed in a hollow shape. One of the coil springs (101) is supported by a closing member (97) that seals the internal space (95) of the rotor (7) with respect to the pump chamber, and the other is supported by a component (91'c). . By the coil spring (101), the component (91'c) is pushed to the position shown in FIG. 5 on the left side. When pressure is formed on the left side of the clutch flange (105) of the component (91′c), the clutch piston (91c) is pushed to the right against the force of the coil spring (101), and the rotating shaft (15 ).

  From FIG. 5, it is clear that the sleeve-like component (91a) of the clutch body (91) includes a recess (67) extending in the direction of the rotating shaft (15). The first end (65) of the coil spring (21) is engaged with the recess (67).

  FIG. 6 is a perspective view of the clutch body (91) of the pump (1) shown in FIG. Since the same reference numerals are given to the same members, reference to the description of the above-mentioned specification regarding FIG. 5 and other drawings is urged to this extent.

  The clutch body (91) includes two sleeve-like parts (91a) and (91b). Clearly visible are a central shaft of the clutch body (91) and a recess (67) extending further in the direction of the rotary shaft (15). The second part (91b) of the clutch body (91) includes a recess (73) extending at a constant angle with respect to the rotation shaft (15). A clutch pin (111) that protrudes from the clutch piston (91 ') and faces radially outward is engaged with the recess (73). When the clutch piston (91 ′) moves in the direction of the rotation axis (15) with respect to the components (91a) and (91b) fixed in the axial direction, the clutch pin (111) prevents the rotor from rotating. 7) Relative rotation of the other sleeve-like component (91b) occurs with respect to the one sleeve-like component (91a) of the clutch body (91) held within. The coil spring (21) of the coil spring clutch (23) not shown here is engaged with the first recess (67) of the first component (91a) by one end thereof. The second end of the coil spring (21) engages with the opening (113) of the sleeve-like second component (91b), and when the component (91b) rotates, In contrast, it moves in the recess (67) extending in the circumferential direction.

  Therefore, when pressure is formed on the side (115) of the viewer looking at the clutch flange (105), the clutch piston (91 ') moves along the rotation axis (15) upward in the right side in FIG. Thereby, a clutch pin (111) moves to the direction of a rotating shaft (15). Since the clutch piston (91 ′) is supported on the rotor (7) so as to rotate together, the clutch body (91) provided by the clutch pin (111) as a result of the axial movement of the clutch piston (91 ′). Rotation of the sleeve-like second part (91b) occurs. As a result, relative movement of the end of the coil spring (21) fixed to the opening (113) with respect to the other end of the coil spring (21) fixed to the first recess (67) occurs. . When the clutch piston (91 ') moves to the right side, the coil spring (21) is extended to release the coupling of the coil spring clutch (23). This occurs because the coil spring (21) is in contact with the peripheral surfaces of the components (91a) and (91b). In particular, the coil spring (21) is no longer in contact with the inner surface of the clutch bell (81) at its peripheral surface, and this clutch bell (81) is covered with the coil spring (21) by the accommodating portion (89), thereby Obviously, the coil spring (21) contracts so that the housing part (89) can serve as a coupling part.

  When the coil spring (21) is not in contact with the accommodating portion (89), friction force is not transmitted to the rotor (7) from the clutch bell (81) to which rotation is given by the driving device. 1) The clutch is disengaged. To this extent, reference is made to the description of each figure, in particular the description of the above specification relating to FIG.

  FIG. 7 shows another embodiment of the pump (1) in longitudinal section, but the housing shown in FIG. 1 is not described. Since the same reference numerals are given to the same members, reference to the description of the above-mentioned specification relating to FIG. 5 and other drawings is encouraged to this extent.

  The pump 1 has a rotor (7) whose right end (85) is used for accommodating a vane and whose left end is provided with a sleeve-like connecting member, preferably shrink-fitted. That is, the clutch bell (81) loaded with torque from the drive device via the clutch (117) is engaged with the connecting member. Therefore, the clutch bell (81), in the illustrated embodiment, is at least partially housed inside the rotor (7), thereby producing a particularly compact configuration.

  As shown in the present embodiment, the rotor (7) itself can be formed of two parts and have a connecting member (115). However, the rotor (7) and the connecting member (115) can be combined into one member. It is also conceivable that the components are formed as a single component, that is, as a single component.

  A coil spring clutch (23) having a coil spring (21) and a clutch device (37) having a clutch body (91) are located inside the rotor (7). The clutch body (91) includes parts (91a) and (91b) shown as two claw-like bodies that are capable of rotating relative to each other. The clutch device (37) further has a clutch piston (91c) movable in the direction of the central axis (15) of the pump (1) and further of the rotor (7). The clutch piston (91c) has a clutch flange (105) in close contact with the inner surface of the internal space (95) in the rotor (7). In the operating position shown in FIG. 7, the clutch piston (91c) approaches the right side of the inner wall (119) of the rotor (7), and this inner wall (119) is separated from the inner space (95) of the pump chamber.

  The clutch device (37) further includes a retaining ring (121) that is coupled to rotate together with the rotor (7) and the first component (91a). The retaining ring (121) also acts as a stopper for the clutch piston (91c) when moved to the left from the position shown in FIG.

  For example, when the working fluid to which pressure is applied via the pressure line (123) is supplied to a portion between the inner wall (119) and the right front surface (125) of the clutch piston (91c), the clutch piston (91c) is Move to the left from the position shown in FIG. Since this movement is performed against the repulsive force caused by the coil spring (21), there is no need to provide another spring which is realized by the coil spring (101) of each of the above embodiments.

  FIG. 8 is a perspective view of the clutch piston (91c) of the embodiment shown in FIG. 7 of the pump (1). Since the same reference numerals are assigned to the same members, the description in the above specification is referred to.

  From FIG. 8, the parts (91a) and (91b) shown as two claws can be seen. The right part (91a) is provided here at least one for engaging with the main body of the part (91a), for example, via a claw part (127) extending parallel to the rotating shaft (15), It is held so as to rotate together with the holding ring (121). Thereby, axial fixation is not performed.

  Again, the clutch piston (91c) with the clutch flange (105) can be seen. The retaining ring (121) and / or the first component (91a) has a first recess (67) with which a first end of a coil spring (21) not shown is engaged. The second part (91b) can rotate with respect to the control piston (91c). The control piston (91c) is slidable in the axial direction with respect to the second component (91b) having the second recess (73) with which the second end of the coil spring (21) is engaged. When the movement of the first part (91a) on the right side with respect to the second part (91b) that cannot be separated toward the right side in the axial direction shown in FIG. 7 occurs via the control piston (91c). Due to this, a component (91b) whose rotational direction is fixed via contact surfaces (91′a) and (91′b) that spread at a certain angle with respect to the rotation axis (15) ( A relative rotation with respect to 91a) and a relative rotational movement of both ends of the coil spring (21) occur.

  Therefore, when the control piston (91c) moves to the left from the position shown in FIG. 8, the first component (91a) is also moved to the second component (91b) fixed in the axial direction to the clutch bell (81). On the other hand, it moves to the left along the rotation axis (15). At this time, rotation of the first component (91a) inside the rotor (7) is hindered by the claw portion (127). As a result, the contact surface (91'a) rotates the second component (91b) inside the rotor (7), and at this time, the movement of the second recess (73) causes one end of the coil spring (21) to move. On the other hand, the second end of the coil spring (21) is held so as to rotate together with the holding ring (121) or the first component (91a). When the first component (91a) moves to the left side of FIG. 8, the coil spring (21) is extended by relative rotation between the component (91a) and the component (91b), so that the peripheral surface thereof is expanded. It is not in the state of frictional coupling with the accommodating portion (89) provided in the clutch bell (81) shown in FIG. Thus, the coupling of the coil spring clutch (23) is released. That is, the torque provided to the clutch bell (81) can no longer be introduced into the rotor (7) via the coil spring (21). Then, the clutch of the pump 1 is disengaged.

  In order to disengage the clutch of the coil spring clutch (23), the pressure between the inner wall (119) and the clutch piston (91c) is finally reduced, the coil spring (21) finally becomes the clutch piston (91c), and further the first The part (91a) is gradually decreased until it is moved to the left side. As a result, the end of the coil spring (21) located in the recess (73) is twisted with respect to the end located in the recess (67), so that the coil spring (21) extends, and this coil spring ( 21) The outer diameter part located in the accommodating part (89) engages with the inner surface of the clutch bell (81). As a result, the clutch of the coil spring clutch (23) is disengaged.

  From FIG. 7, it is possible to fill the right front surface (125) with a pressurized working fluid, and therefore utilize a relatively large surface to apply force against the clutch piston (91c). It is clear that this is possible. The coil spring (21) is sufficiently preloaded so that only the rotation is applied without being pulled in the longitudinal direction when the clutch piston (91c) operates.

  FIG. 9 shows yet another embodiment of the pump (1) in longitudinal section, but the housing shown in FIG. 1 is not described. Since the same reference numerals are given to the same members, in this limit, the description in the above-mentioned specification relating to each drawing is referred to.

  The pump includes a rotor (7) partially engaged with a clutch bell (81). The rotor (7) is formed on its right end (85) so that vanes are available for the production of the pump (1). The left end (87) is formed in a hollow shape and surrounds the coil spring (21) of the coil spring clutch (23). The rotor (7) is further provided with a clutch device (37) that works together with the coil spring (21). The clutch device (37) includes a clutch body (91) formed of two parts and including a clutch portion (91 ″ a) and a clutch member (91 ″ b) rotating therewith.

  The coil spring (21) is formed so as to be retractable in the first internal space (95-1) of the rotor (7). The clutch member (91 ″ b) is accommodated in the space surrounded by the coil spring (21). The first end of the coil spring (21) is connected to rotate with the clutch member (91 ″ b), and the second end is connected to rotate with the rotor (7). . The clutch portion (91 ″ a) is rotatably stored in the second internal space (95-2) of the rotor (7).

  When the coil spring (21) is fixed on the clutch member (91 ″ b), there is no frictional connection with the inner surface of the accommodating portion (89) of the clutch bell (81). That is, the coupling of the coil spring clutch (23) is released. However, when the coil spring (21) is extended, the coil spring (21) is in frictional connection with the accommodating portion (89) of the clutch bell (81) that acts as a coupling portion, and the clutch is attached to the clutch bell (81) by the driving device. The introduced torque can be transmitted to the rotor (7) via the coil spring (21).

  The actuating device (37) is described in more detail as follows based on FIG.

  FIG. 10 is an exploded view of the pump (1). Since the same reference numerals are given to the same members, the above description is referred to.

  Each component of the pump (1) is provided concentrically with the rotating shaft (15). That is, the clutch bell (81) can be seen on the lower left side, and the clutch member (91 ″ b) can be seen on the right side. A coil spring (21) is shown at a position adjacent to this. The rotor (7) is formed from two parts. The sleeve-shaped first rotor member (7-1) accommodates the coil spring (21) in at least a part thereof. From FIG. 9, the first internal space in which the sleeve-like first rotor member (7-1) is separated from the second internal space (95-2) in the rotor (7) via the wall portion (129). It is clear that (95-1) is included. A clutch portion (91 ″ a) of the clutch member (91 ″ b) is provided in the second internal space (95-2). The clutch portion (91 ″ a) includes at least one vane (131) and (133) provided at two positions opposed to each other in the radial direction in the drawing, and the vane (131), (133) is in contact with the inner surface of the sleeve-like rotor member (7-1) by the surface in the longitudinal direction opposite to the rotating shaft (15), and is separated from the pressure chamber.

  When pressure is applied to the side surface of at least one vane, the vane rotates around the rotation axis (15) in the first direction. When pressure is applied to the other side, the vane rotates in the opposite direction.

  In the embodiment shown here, the rotor (7) also includes a rotor portion (7-2) used to accommodate vanes or other pump components. On the side surface of the sleeve-shaped first rotor member (7-1) side, at least one, here two stopper members (135) provided at a certain distance from the rotor portion (7-2), (137) extends. The peripheral surfaces of the stopper members (135) and (137) are in close contact with the inner surface of the internal space (95-2) of the sleeve-shaped first rotor member (7-1). Therefore, between the two stopper members (135) and (137), the vanes (131) and (133) perform the above rotational movement, and the inner surfaces of the stopper members (135) and (137) are the vanes (131). ), (133) is formed to limit the movement.

  One end of the coil spring (21) engages with the rotor (7), and the other end is a recess provided on the second part of the clutch body (91), that is, the clutch member (91 ″ b). Engage with (139).

  In order to operate the coil spring clutch (23), each side of the clutch vane (91 ″ a) is filled with a working fluid under pressure so that at least one vane, here the vane (131) is filled. ) And (133) rotate in one direction. A clutch coupled to rotate with a coupling pin (141) via, for example, a dihedron (143) via a coupling pin (141) coupled to rotate with the vanes (131), (133). Part (91 ″ b).

  In the following, the control of the coil spring clutch (23) will be described in more detail. When no pressure is applied to at least one vane, here, the vanes (131) and (133), the clutch vane (91 ″ a) has the plurality of vanes caused by the repulsive torque of the coil spring (21). It rotates toward its starting position until it comes into contact with the stopper members (135), (137). In this operating position, the torque is transmitted to the rotor (7) by the peripheral surface of the coil spring (21) coming into contact with the inner surface of the accommodating portion (89) of the clutch bell (81). When the clutch of the pump (1) is to be disengaged, one of the side surfaces of the vanes (131) and (133) is filled with a working fluid under pressure, such as oil, so that these vanes are coil springs. It rotates in a predetermined direction with respect to the repulsive torque of (21). The coil spring (21) is positioned on the circumferential surface of the clutch member (91 ″ b) by the rotational movement, and the circumferential surface is extended so as not to be frictionally coupled to the inner surface of the accommodating portion (89). To do. As a result, the clutch of the pump (1) is disengaged.

  It is highly conceivable to reverse the clutch function of the coil spring clutch (23). Therefore, the coil spring (21) is positioned on the circumferential surface of the clutch member (91 ″ b) in the non-pressure state of the vanes (131) and (133), and the accommodating portion (89) of the clutch bell (81). It is also possible for the situation not to engage with the inner surface. Therefore, the clutch of the pump (1) is disengaged in the non-pressure state. When the clutch of the pump (1) is to be connected, a pressure is applied to one of the side surfaces of the vanes (131) and (133), thereby rotating the clutch portion (91 ″ a). As a result, the clutch member (91 ″ b) rotates, and, in this way, in the design in which the coil spring (21) is a coil spring clutch (23), the accommodating portion (89) of the clutch bell (81). ) And the engaged state. Thus, the pump (1) operates only when pressure is applied to at least one of the vanes (131) and (133).

  In the illustrated embodiment, no separate repulsion member is required for the purpose of rotating the clutch vane (91''a) to its desired operating position. The coil spring (21) is designed to apply a direct repulsion torque.

  FIG. 11 shows another embodiment of the pump in longitudinal section. Again, the housing shown in FIG. 1 is omitted. The pump is provided with a rotor (7) whose right end (85) is designed to be able to work with at least one vane for the purpose of supplying fluid. At least a part of the left end portion (87) enters the clutch bell (81). The rotor (7) is formed in a hollow shape. Here, the inner space (95) is sealed with respect to the right side by a closing member (97), so that the inner space is connected to the pump chamber. Not in fluid coupling. The internal space (95) is divided into two parts by the wall (129). The first part (95a) stores the elastic member formed here as the coil spring (101), and the second part (95b) stores the coil spring (21) of the coil spring clutch (23). ing. The coil spring protrudes from the rotor (7) into the accommodating portion (89) of the left clutch bell (81). The inner diameter of the housing part (89) is adjusted in accordance with the outer diameter of the coil spring (21). As a result, when the coil spring (21) is in the first operating position, the inner surface of the housing part (89) by the peripheral surface thereof. In the second operation position, the inside of the housing part (89) can be freely rotated so that the friction torque is not transmitted.

  The pump (1) includes a clutch body (91) having a clutch device (37). The clutch body (91) is movable in the axial direction, that is, in the direction of the rotating shaft (15), and further toward the position shown in FIG. 11, that is, the first operating position on the left side by the coil spring (101). Pushed. The clutch body (91) comprises two parts, in particular a clutch flange (105) which is formed as a piston and is in close contact with a first part (95a) of an internal space (95) provided in the clutch body. A first component (91a) is provided.

  The first part (91a) of the clutch body (91) passes through the clutch bell (81). The end portion is provided with a receiving portion (145) formed as a retaining ring here. The first part (91a) is rotatably supported by a drive member (147) in which a drive torque is applied to a free end protruding from the clutch bell (81). The drive member (147) is connected to rotate together with the clutch bell (81). The free end of the drive member (147) can be formed, for example, as a tetrahedron (149). The drive member (147) enters the inside of the coil spring (21) and is provided with an outer tooth portion (151) at an inner end portion thereof, and the outer tooth portion (151) is also provided with a clutch ring (153) provided with teeth. ). The clutch ring (153) is configured to be freely rotatable inside the clutch bell (81). The clutch ring (153) is further connected to rotate together with the coil spring (21). The other end of the coil spring (21) is connected to rotate together with the rotor (7).

  The first part (91a) includes a clutch shoulder (155) against which the drive member (147) abuts. In the operating position of the first part (91a) of the clutch body (91) shown in FIG. 11, the clutch shoulder (155) pushes the drive member (147) completely to the left side, and its outer teeth (151) is coupled to the clutch ring (153). It becomes clear that the left end portion of the drive member (147) is provided at a distance (157) from the receiving portion (145).

  FIG. 12 is an exploded view showing each member of the pump (1), particularly the clutch body (91), the drive member (147), and the clutch ring (153). Since the same reference numerals are given to the same members, the above description regarding each figure is urged to be referred to in this limit.

  Here, the clutch body (91) has a clutch flange (105) at one end, here the right end, and the first part (91a) of the clutch body (91) is a tetrahedron ( It is clear that it is gripped by a drive member (147) with 149). A receiving portion (145) provided at a distance from the front surface (159) of the drive member (147) is arranged at the end of the first clutch portion (91a) opposite to the clutch flange (105). ing.

  The end of the drive member (147) facing the front surface (159) has an annular main body (161) here, and a tooth portion (163) protruding from the main body to the left in parallel to the rotation axis (15). ) Having outer teeth (151).

  The clutch ring (153) also has a main body (165), and a tooth portion (167) protrudes from the main body (165) toward the right side. The tooth portion (167) also extends parallel to the rotation axis (15). The tooth part (163) of the outer tooth part (151) and the tooth part (167) of the clutch ring (153) have the width and length of the operating position shown in FIG. 11 and the driving member (147 shown in FIG. 12). ) And the clutch ring (153) at the relative positions, both teeth mesh with each other, whereby the torque of the drive member (147) is transmitted to the clutch ring (153) by both teeth. .

  The following points become clear from FIGS. 11 and 12.

  When the clutch flange (105) receives a compressive force formed by the working fluid, the coil spring (101) pushes the clutch member (91) completely to the left as shown in FIG. Thus, the clutch flange (105) contacts the wall (129). The drive member (147) is moved completely to the left by the clutch shoulder (155), so that the tooth portion (163) of the outer tooth portion (151) is engaged with the tooth portion (167) of the clutch ring (153). .

  This time, when torque is applied to the drive member (147), this torque is transmitted to the clutch ring (153) via the teeth (163) and (167). The clutch ring (153) is freely rotatable with respect to the clutch bell (81). At this starting position, therefore, when no drive torque is introduced, the coil spring (21) of the coil spring clutch (23) is not in contact with the inner surface of the housing (89). 21) does not transmit any torque to the clutch bell (81). Here, when torque is introduced into the clutch ring (153), the coil spring (21) transmits this torque to the rotor (7). If the torque of the drive member (147) occurs very rapidly and / or because the working fluid supplied by the pump is cold and viscous, for example, a large equilibrium force is applied to the right end of the rotor (7) ( 85), the coil spring (21) extends when the torque is introduced into the clutch ring (153), so that its peripheral surface engages with the inner surface of the accommodating portion (89), Further, torque is transmitted to the clutch bell (81). The rotor (7) is rotatably supported by the clutch bell (81).

  When only a small amount of torque is transmitted from the clutch ring (153) to the rotor (7), the coil spring (21) does not expand, and the coil spring (21) is caused to have a clutch bell (81 by its peripheral surface. ) Is not in contact with the inside of the housing part (89).

  To disengage the coil spring clutch (23), the clutch device (37) is operated. For this purpose, pressure is formed on the left side of the clutch flange (105) in the first part (95a) of the internal space (95) in the rotor (7) or on the right side of the clutch flange (105). A negative pressure is formed in Thus, the clutch flange (105) finally moves to the right against the repulsive force of the coil spring (101), and the first component (91a) also moves together with the clutch flange (105). Since the component (91a) extends in the drive member (147) with little friction, the component (91a) may first change in the axial position of the drive member (147). Move to the right. That is, the initial movement of the clutch flange (105) does not result in a change in the position of the drive member (147) or tooth (163) relative to the tooth (167).

  Since the receiving part (145) of the first component (91a) is provided at a constant interval (157) with respect to the front surface (149) of the drive member (147), the clutch flange (105), and further The one component (91a) can move a very long distance toward the right side until the receiving portion (145) contacts the drive member (147). Only when the clutch flange (105) further moves to the right is the drive member (147) simultaneously moved to the right. Depending on the length of the teeth (163) and teeth (167) measured in the direction of the axis of rotation (15), the drive member (147) along with its outer teeth (151) and outer teeth (151) And the clutch ring (153) are moved to the right by a certain distance until the mechanical coupling, that is, the complete engagement is released. In this case, no further torque is transmitted from the drive member (147) to the clutch ring (153) via the tooth portion (163) and the tooth portion (167). Thus, no further torque is applied to the left end of the coil spring (21) connected to the clutch ring (153) shown in FIG. Thus, the clutch of the pump (1) is disengaged. No further torque acts on the rotor (7).

  This time, when the force acting on the clutch flange (105) becomes small, whether the pressure on the left side of the clutch flange (105) or the negative pressure on the right side of the clutch flange (105), the coil spring (101) As a result, the clutch body (91), and therefore the first part (91a), also moves to the left. In the first movement section, the clutch shoulder (155) does not contact the end of the drive member (147) facing the front surface (159). Only after a certain pressure change is exceeded, the clutch shoulder (155) contacts the drive member (147), and then the compression force of the coil spring causes the drive member (147) to move to the outer teeth (151). The left tooth portion (163) is moved to the left until it engages with the tooth portion (167) of the clutch ring (153). At this time, torque is transmitted to the coil spring (21) for the first time. The coil spring (21) does not extend until a certain torque is reached, and transmits the torque introduced into the drive member (147) directly to the rotor (7). When a greater resistance force acts on the rotor (7), the coil spring (21) extends until the peripheral surface thereof is in frictional contact with the inner surface of the accommodating portion (89) of the clutch bell (81). To do.

  When the coil spring clutch (23) is completely connected, the clutch body (91) is in the position shown in FIG. 11, so that the receiving portion (145) is located on the front surface ( 159) and a fixed interval (157).

  When the coil spring clutch (23) is to be disconnected again, the clutch flange (105) is moved to the right until the receiving portion (145) contacts the front surface (159) of the drive member (147). At this time, the release of the coupling between the tooth portion (163) and the tooth portion (167) is started for the first time.

  Therefore, there is a hysteresis characteristic of the clutch that can be adjusted by the distance (157) between the receiving portion (145) and the front surface (159) of the drive member (147), and further by the force of the coil spring (101) acting as a repulsion spring. Occur.

  After all, torque can be transmitted from the drive member (147) to the rotor (7) only through the coil spring (21), but the peripheral surface of the coil spring (21) and the clutch bell (81). ) Can also be performed by friction torque acting additionally between the inner surface of the housing portion (89). If the torque transmitted is small, this torque can be transmitted exclusively via the coil spring (21).

  When the complete engagement between the clutch ring (153) and the outer teeth (151) of the drive member (147) is broken, the coil spring (21) relaxes and reaches its rest position to extend further. There is no longer to do. Therefore, no coupling by force distribution, that is, friction coupling occurs between the coil spring (21) and the accommodating portion (89) of the clutch bell (81). Therefore, the clutch of the pump (1) is disengaged.

  FIG. 13 shows a part of the pump (1) in a longitudinal section. Again, the pump housing shown in FIG. 1 is omitted. The same members are given the same reference numerals, and as long as this is the case, the description in the above specification is referred to.

  The pump (1) includes a rotor (7) that is configured to allow its right end (85) to work with at least one vane for the supply of fluid. The left end portion (87) of the rotor (7) protrudes into the clutch bell (81) where the drive torque is introduced. The rotor (7) is rotatably supported by a clutch bell (81). The clutch bell (81) is rotated by a driving device and continuously operates simultaneously.

  The pump (1) includes a coil spring clutch (23) having a coil spring (21) and a clutch device (37). The clutch device (37) is located inside the hollow rotor (7) together with the coil spring clutch (23), and the coil spring (21) and the clutch device (37) protrude into the clutch bell (81). That is, the whole is not accommodated in the rotor (7).

  The clutch device (37) includes a clutch body (91) having a first part (91a) formed as a hydraulic piston and a second part (91b) formed as a friction clutch. The second part (91b) has a conical outer surface (169) that works with the conical inner surface (171) of the clutch bell (81).

  The two parts (91a), (91b), the rotor (7), and the clutch bell (81) are arranged concentrically with respect to the rotating shaft (15).

  The first part (91a) of the clutch body (91) includes a clutch flange (105) whose peripheral surface is in close contact with the inner surface of the recess (95) of the rotor (7). The part of the first component (91a) in contact with the clutch flange (105) accommodates the coil spring (21) on its peripheral surface, that is, the coil spring (21) is in its first operating position. In this case, the outer diameter of the clutch flange (105) is selected so as not to be in a state of friction welding with the inner surface of the recess (95). The coil spring (21) is connected to rotate together with the rotor (7). The other end engages with a recess (67) extending in the direction of the rotation axis (15) in the circumferential surface of the first component (91a), and is held so as to rotate therewith.

  In the example shown in FIG. 13, the clutch body (91) formed as a hydraulic piston is in the right operating position. The operating position on the right side is a position pushed by an elastic member, here a coil spring (21). Thereby, the outer surface (169) of the second part (91b) of the clutch body (91) is pressed against the conical inner surface (171) of the clutch bell (81). That is, the torque introduced into the clutch bell (81) is transmitted to the clutch body (91) through the frictional coupling described in the present invention. Since the clutch body is connected to rotate together with one end of the coil spring (21), the rotor (7) has a coil spring (when the transmitted force does not exceed a certain upper limit). Rotate only by the force provided by 21). However, when the transmitted force is larger, the coil spring (21) is extended, and the peripheral surface thereof is in frictional engagement with the inner surface of the accommodating portion (89) of the clutch bell (81). become. Therefore, torque is transmitted not only through the coil spring (21) itself but also through the clutch bell (81).

  From FIG. 13, it is clear that the right end portion of the coil spring (21) has a wider width, that is, the coils have a larger distance from each other. This coil spring (21) is here formed as a compression spring (173) so as to improve the repulsive force of this coil spring (21) and in particular to make it possible not to use the coil spring (101). Has been.

  The friction clutch generated between the clutch body (91) and the clutch bell (81) can be released by moving the clutch body (91) to the left from the position shown in FIG. Thereby, a coil spring (21) is compressed with the part currently formed as a compression spring (173). At the same time, the conical outer surface (169) of the second part (91b) of the clutch body (91) is separated from the conical inner surface (171) of the clutch bell (81). Here, since the coil spring (21) can relax and reach its rest position, the frictional coupling between the peripheral surface and the inner surface of the accommodating portion (89) of the clutch bell (81) is There can be no more. Therefore, the pump (1) is disconnected from the drive device.

  FIG. 14 is a perspective view showing the coil spring (21) in a greatly enlarged manner. On the upper right side, the coil part further spaced apart, that is, the part forming the compression spring (173) can be seen. The coil spring (21) is fixed in the rotor (7) in the axial direction and tangential direction by the annular portion (175) protruding radially outward, and this rotor (7) is surrounded by the inner space (95). Corresponding recesses are provided at suitable positions on the inner wall.

  The end (177) of the coil spring facing the compression spring (173) is provided with a projecting portion (179) projecting radially inward, which cannot be seen here, and this projecting portion (179) is shown in FIG. 13 is engaged with the recess (67) shown in FIG. 13, thereby causing coupling with the clutch body (91).

  FIG. 15 shows a modified embodiment of the coil spring (21) in a side view. A plurality of coils at the end of the coil spring are arranged at a larger distance from each other for the purpose of forming a compression spring (173). The coil spring (21) thus formed can be used for an embodiment of the pump (1) formed, for example, similar to that shown in FIG. Here, it is obvious that a coil formed as a compression spring (173) at the end and having an outer diameter matched to the inner cone functions as a friction clutch.

  In a state where the clutch is connected, the conical outer surface of the compression spring (173) is in contact with the conical inner surface of the drive device, for example, the clutch bell.

  When the free end (181) of the conical compression spring (173) moves in the resting direction of the left coil spring (21), the cone angle generated at the compression spring (173) increases. The hypothetical cone (187) is shown using a dotted line, which shows the coil circumference of the compression spring (173) on the inner surface of the cone (173) with the compression spring (173) not compressed. 183) is located. When the free end (181) of the compression spring (173) is moved to the left, a cone (185) indicated by a broken line is produced, and this opening angle is larger than that of the cone (187) indicated by a dotted line.

  When the compression spring (173) is distorted by compression in the direction of the rotation axis (15) coinciding with the central axis of the coil spring (21), the peripheral surface (183) of the compression spring (173) is indicated by a dotted line. The inner conical surface (187) indicated by is not touched. Therefore, the movement of the free end (181) to the other part of the coil spring (21) results in the release of the friction clutch formed by the peripheral surface (183) of the compression spring (173).

  The movement of the free end (181) of the compression spring (173) can on the one hand be caused by a force acting from the right. However, it is also conceivable that one member reaches the free end (181) from the internal space of the coil spring (21) and that this member moves to the left to disengage the friction clutch.

  In summary, based on FIG. 15, the free end (181) of the coil spring (21) can be formed as a compression spring (173), and its conical circumferential surface (183) is the cone of the friction clutch. It is clear to cooperate with the inner surface of the shape. When the length measured in the axial direction of the compression spring (173) is shortened by the movement of the free end (181), the circumferential surface (183) of the compression spring (173) and the inner cone of the friction clutch In this case, it is impossible to transmit any more torque from the drive unit to the rotor by giving up generating frictional coupling.

  Therefore, the coil spring (21) can also be formed as a clutch.

  From the description of the pump (1), the pump (1) can use the coil spring clutch (23) and the clutch device (37) to disengage the clutch even when drive torque is present. . The release of the coil spring clutch (23) can also be performed using a working fluid to which pressure is applied. However, it is highly likely that the negative pressure will be used to cause the clutch (1) to engage and disengage the clutch. Therefore, when the pump (1) is used in a vehicle for the purpose of generating a negative pressure, the generated negative pressure causes the coil spring clutch (23) to be turned on when the desired negative pressure value is achieved. Used to activate and thereby disengage the pump (1) clutch. As described with reference to FIGS. 11 and 12, a particularly preferable clutch behavior of the clutch occurs when the clutch behavior having a hysteresis characteristic is realized.

  In summary, it is clear that the pump (1) can be formed very easily and compactly, so that this pump (1) has almost no possibility of failure and is inexpensive to manufacture. It is characterized by.

DESCRIPTION OF SYMBOLS 1 Pump 3 Housing 5 Pump chamber 7 Rotor 9 Oil pump 11 Piping 13 Hole part 15 Rotating shaft 17 Bearing protrusion part 19 Projection part 21 Coil spring 23 Coil spring clutch 25 Shaft journal 27 Extension part 29 Concave part 31 Retaining ring 33 Groove part 35 Groove part 37 Clutch device 39 clutch sleeve 41 left end portion 43 annular bead 45 inner surface 47 front surface 49 seal plate 51 inner edge portion 53 circumferential surface 55 chamber 57 hole portion 59 pipe 61 coil spring 63 clutch surface 65 first end portion 67 first recess portion 69 wall portion 71 Second end portion 73 Second recess portion 77 Measuring tube 79 Valve device 80 Tank 81 Clutch bell 83 Bearing 85 Right end portion 87 Left end portion 89 Housing portion 91 Clutch body 93 Screw 95 Internal space 97 Closure member 99 Hollow space 101 Carp Spring 103 Inner wall 105 Clutch flange 107 Gap 109 Bearing 111 Clutch pin 113 Opening part 115 Connecting member 117 Clutch 119 Inner wall 121 Holding ring 123 Pressure line 125 Right front 127 Claw part 129 Inner wall 131 Vane 133 Vane 135 Stopper member 139 Stopper member 139 141 connecting pin 143 dihedral body 145 receiving portion 147 drive member 149 tetrahedral body 151 outer tooth portion 153 clutch ring 155 clutch shoulder portion 157 interval 159 front surface 161 main body 163 tooth portion 165 main body 167 tooth portion 169 conical outer surface 171 conical outer surface 171 173 Compression spring 175 Annular part 177 End part 179 Projection part 181 Free end part 183 Circumferential surface 185 Conical surface 187 Inner conical surface

Claims (20)

A base over emission type vacuum pump for the brake force booster of the vehicle,
The pump is
A rotor (7) to which rotational driving is applied from a driving device via a coil spring clutch (23);
A clutch device (37);
The clutch device releases or connects the rotor (7) from the driving device by extending the coil spring (21) in the first operating position, and also via the coil spring (21) in the second operating position. Connecting or disconnecting the rotor (7) and the drive device ;
The pump includes a clutch bell (81), and the clutch device (37) includes a first part (91a) serving as a hydraulic piston and a second part (91b) serving as a friction clutch. The second part (91b) is defined and provided with a conical outer surface (169), which acts with the conical inner surface (171) of the clutch bell (81), whereby the first and second The components (91a, 91b), the rotor (7), and the clutch bell (81) are arranged concentrically with the rotating shaft (15) of the rotor (7). Features a pump. Wherein said clutch body (91) is movable by hydraulic vane-type vacuum pump according to claim 1. The clutch device (37) comprises a resilient member the said elastic member is made possible in that the clutch body (91), the front Symbol coil spring (21) is connected to the rotor (7) the driving device The vane type vacuum pump according to claim 1 or 2 , wherein the vane type vacuum pump is pushed up to two operating positions. The vane type vacuum pump according to any one of claims 1 to 3 , wherein the clutch device (37) performs switching depending on the pressure inside the brake force booster of the vehicle. 5. The vane type vacuum pump according to claim 4 , wherein the driving device of the pump is cut off when a desired negative pressure is achieved inside the braking force booster of the vehicle. The vane type vacuum pump according to claim 7 or 8, further comprising an oil supply device that is shut off together with the driving device of the rotor (7). The clutch device (37) includes a 4 / 2-way valve for controlling the pressure chamber and the oil supply device of the pump (1),
A state wherein the oil supply device or the pressure chamber is no load pressure, while the front Kiben is connected to the tank (80) of the oil supply pump (9), said pressure chamber or the oil supply device The vane type vacuum pump according to any one of claims 1 to 6 , wherein the vane type vacuum pump is connected to an oil supply pump (9). The vane-type vacuum pump according to any one of claims 1 to 7 , wherein the clutch device (37) includes a clutch body (91). The vane-type vacuum pump according to claim 8 , characterized in that the clutch body (91) is formed of two parts. Wherein the rotor (7), and providing a movable drive member (147) in the direction of the rotational axis of the rotor (7) (15), in any one of claims 1 to 9 The vane type vacuum pump as described. The vane-type vacuum pump according to claim 10 , wherein the clutch body (91) is connected to the drive member (147). The vane-type vacuum pump according to claim 11 , wherein the clutch has an axial play, and the play causes a hysteresis characteristic of the clutch. The vane type vacuum pump according to any one of claims 1 to 12 , wherein a friction clutch is provided between the driving device (81) and the clutch body (91). The vane-type vacuum pump according to any one of claims 1 to 13, characterized in that the coil spring (21) is formed as a compression spring (173). The vane-type vacuum pump according to claim 14 , wherein the coil spring (21) includes a plurality of coils at least partially in the axial direction having a larger interval than the others. 16. The vane type vacuum pump according to claim 14, wherein the axial length of the compression spring (173) can be changed by the action of a force on the free end (181). The vane-type vacuum pump according to claim 16 , characterized in that the coil spring (21) includes a portion having a conical surface. The vane type vacuum pump according to claim 17 , wherein the portion is formed as an outer cone having a constant opening angle. 19. The vane type vacuum pump according to claim 18 , wherein the opening angle is expandable by movement of the free end (181) of the compression spring (173). Characterized in that said conical portion of said coil spring (21) is part of a friction clutch, the vane type vacuum pump according to claims 17 to 19.

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