JP5412366B2 - Hydraulic supply device for transmission - Google Patents

Description

  The present invention relates to a hydraulic pressure supply device for a transmission including an auxiliary oil pump such as an electric oil pump in addition to a main oil pump in a hybrid vehicle or the like. In particular, the present invention relates to the structure of a ball-type counter-support valve that is provided to block the flow of oil from a main oil pump to an auxiliary oil pump.

  Recently, every time a vehicle is stopped due to a signal or the like, the engine is automatically paused to improve fuel efficiency and to suppress carbon dioxide emission. For example, a vehicle equipped with a hybrid vehicle or an idling stop engine, etc. Are known. An automatic transmission (AT) mounted on these vehicles is provided with a mechanical oil pump (main oil pump) that supplies oil (AT fluid) to a hydraulic control device of the transmission in conjunction with the engine. It has been. That is, since the mechanical oil pump does not drive unless the engine is started, some mechanical oil pumps do not supply oil to the hydraulic control device when the engine is stopped. Therefore, for example, in a hybrid vehicle that can start without starting the engine, an electric oil pump (auxiliary oil pump) for supplying oil to the hydraulic control device is supported even when the engine is not started. Provided. As an example of such a thing, many things, such as the apparatus described in patent document 1, for example, are known.

  This patent document 1 discloses a first oil pump (main oil pump) driven by a main shaft of a transmission, a second oil pump (auxiliary oil pump) driven by an electric motor, and discharge of the second oil pump. A transmission hydraulic pressure supply device including a ball-type counter-support valve provided between the first oil pump and the discharge side of the first oil pump for blocking the flow of oil from the first oil pump to the second oil pump. It is disclosed.

  A conventional structure of the ball-type reversely supported valve will be described with reference to FIG. FIG. 3 is an enlarged cross-sectional view showing an example of a ball-type counter-support valve included in a conventionally known transmission hydraulic pressure supply device. The ball-type counter-support valve 1 is formed in a cylindrical shape with both ends open, and is fixed to the transmission case T and a mounting hole Ta formed in the transmission case T as shown in FIG. 2 It is accommodated in an attachment hole 6a formed in the oil pump base 6 (attachment member) of the oil pump assembly. When the ball-type counter-support valve 1 is accommodated in one case (or space) composed of the two members, the ball-type counter-support valve 1 is brought into contact with the opposing ends of the transmission case T and the oil pump base 6. It is arranged so as to straddle the boundary surface X (also referred to as a mating surface). In addition to the ball-type reverse support valve 1, a mounting hole Tb is formed in the transmission case T, and a mounting hole 6b is formed in the oil pump base 6, respectively. It is possible to accommodate a suction pipe 3 (also called a suction pipe) used in combination with 1.

  The ball-type counter-support valve 1 is provided with a press-fitting portion A for press-fitting a stopper pin S for limiting the stroke amount of the ball B that can move left and right inside the cylinder from the outside of the cylinder. Since the stopper pin S is press-fitted from the outside of the cylinder in this way, especially when a high hydraulic pressure is applied to the ball-type counter-support valve 1, the gap between the stopper pin S and the press-fit portion A is particularly important. The oil flowing inside the cylinder leaks to the outside of the cylinder and further to the first oil pump side and the second oil pump side (not shown) through a slight gap that can occur in the cylinder, making it impossible to perform proper hydraulic pressure control. There is a fear. Therefore, conventionally, in order to prevent such oil leakage from the stopper pin S (press-fit portion A), cylinders on the sides close to the first oil pump and the second oil pump with the stopper pin S (press-fit portion A) as a base point. O-rings 2a and 2b (seal rings) are arranged on the outer periphery.

Patent No. 4205026

  However, in the structure of the ball-type reversely supported valve 1 in which the O-rings 2a and 2b (seal rings) are arranged on the outer peripheral portions of the cylinders close to the first oil pump and the second oil pump with the stopper pin S as described above as a base point, The oil is not prevented from leaking from the mating surface X of the transmission case T and the oil pump base 6 to the outside of the case or the suction pipe 3 side (see arrows in the figure). In particular, the mating surface X is a boundary portion where two different members are in contact with each other and is connected to the outside of the case and the suction pipe 3, where oil is more likely to leak than the first oil pump side and the second oil pump side. It is. Therefore, the oil leakage from the mating surface X has a large amount of leakage compared to the oil leakage to the first oil pump side and the second oil pump side, and can have a great influence on the fact that proper hydraulic control cannot be performed. is there.

  Therefore, in the conventional apparatus, oil leakage from the mating surface X to the outside of the case is prevented by separately arranging an O-ring 2c on the mating surface X. However, an O-ring 2c is prepared separately. The cost is increased because the number of parts is increased and the O-ring 2c prepared separately needs to be processed so as not to leak oil on at least one of the transmission case T and the oil pump base 6. It is inconvenient. Further, since the O-ring 2c is disposed on the outer periphery so as to surround the ball-type counter-support valve 1 and the suction pipe 3, oil leakage from the mating surface X to the suction pipe 3 side is not prevented.

  The present invention has been made in view of the above-described points, and the oil flowing inside the ball type counter-support valve leaks from the mating surface of the transmission case and the oil pump base to the outside of the case and the suction pipe without cost. It is an object of the present invention to provide a hydraulic pressure supply device for a transmission that is prevented from coming out.

The transmission hydraulic pressure supply device according to the present invention includes a first oil pump driven by a transmission main shaft, at least one second oil pump (P) driven by appropriate means (7), and the first oil pump (P). 2 an attachment member (6) for removably attaching the oil pump (P) to the transmission case (T) from the outside of the transmission, a discharge side of the first oil pump, a discharge side of the second oil pump (P), Between the first oil pump and the second oil pump (P), a cylindrical ball-type reverse valve (1) provided to block the ball-type reverse valve (1) ) Is accommodated in a space (Ta, 6a) formed by combining the transmission case (T) and the mounting member (6). In the hydraulic pressure supply device of the transmission in which the discharge side of the first oil pump is connected to the hydraulic pressure control device, the ball-type counter-support valve (1) includes a plurality of seal rings (2b, Ra) on the outer periphery. it has a ball for blocking the flow of oil (B), respectively, mating surfaces between the mounting member and the transmission case (T) (6) and (X), to limit the stroke of the ball (B) And at least one of the plurality of seal rings (2b, Ra) between the first and second stopper pins (S) .

According to the present invention, the oil from the first oil pump to the second oil pump (P) is accommodated in a space (Ta, 6a) formed by combining the transmission case (T) and the mounting member (6). In the cylindrical ball-type reversely supported valve (1) for blocking the flow, a ball for blocking the flow of oil disposed inside the mating surface (X) of the transmission case (T) and the mounting member (6) (B) It arrange | positions so that at least 1 of the some seal ring (2b, Ra) arrange | positioned at an outer peripheral part may be included between the stopper pins (S) for restrict | limiting the stroke amount . In this way, even if the oil flowing through the ball-type counter-support valve 1 leaks through the stopper pin S, the transmission case T housing the ball-type counter-support valve 1 via the mating surface X and the outside of the oil pump base 6 It can be prevented from leaking out. That is, since it is not necessary to arrange a separate seal ring on the mating surface X as compared with the prior art, the number of parts can be reduced, and a separate seal ring is arranged on at least one of the transmission case T and the oil pump base 6. Therefore, oil leakage prevention can be achieved without cost.

  Note that the reference numerals in the parentheses described above exemplify the corresponding constituent elements in the embodiments described later for reference.

According to the present invention, at least of the plurality of seal rings disposed on the outer peripheral portion between the mating surface of the transmission case and the mounting member and the stopper pin that limits the stroke amount of the ball for blocking the oil flow. Since it arrange | positions so that one may be included, there exists an effect that it becomes possible to achieve prevention of an oil leak without incurring cost compared with the past.

It is a side view which shows the transmission which applied the hydraulic pressure supply apparatus of the transmission which concerns on this invention in the state which removed a part of transmission case. It is an expanded sectional view which shows the ball | bowl type reverse support valve contained in the hydraulic pressure supply apparatus of the transmission shown in FIG. It is an expanded sectional view which shows an example of the ball | bowl type reverse support valve contained in the hydraulic supply apparatus of the transmission conventionally known.

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

  FIG. 1 is a side view of a transmission showing a transmission to which a transmission hydraulic pressure supply device according to the present invention is applied. However, here, a state in which a part of the transmission case is removed is shown, and for the convenience of illustration, the illustration of the first oil pump (main oil pump) driven by the main shaft of the engine is omitted.

  As shown in FIG. 1, the second oil pump assembly 5 can be detachably attached to the transmission case T. The second oil pump assembly 5 includes an oil pump base 6 (attachment member), a second oil pump P mounted on the oil pump base 6, and an electric motor 7 that drives the second oil pump P. The second oil pump assembly 5 can be attached by fixing the oil pump base 6 to the transmission case T via a plurality of bolts. After the second oil pump assembly 5 is attached, the mating surface X is formed between the transmission case T and the oil pump base 6 (see FIG. 2).

  The second oil pump P included in the second oil pump assembly 5 can be driven by appropriate driving means such as the electric motor 7 when the first oil pump cannot be driven, for example, when the engine is stopped. Auxiliary oil pump. The appropriate drive means is not limited to the electric motor 7, and may be an appropriate one such as an auxiliary engine provided separately from the main engine that drives the vehicle and the first oil pump.

  The suction sides of the first oil pump and the second oil pump P are connected to a strainer 4 of the transmission. On the other hand, between the discharge side of the first oil pump and the discharge side of the second oil pump P, there is a ball type reverse support valve 1 for blocking the oil flow from the first oil pump to the second oil pump P. It is intervened. This ball-type reverse support valve 1 allows oil to flow from the second oil pump P to the discharge side of the first oil pump, so that the oil discharged from the first oil pump and the oil discharged from the second oil pump P Both are supplied to a hydraulic control device (not shown) of the transmission. That is, oil (ATF) from the strainer 4 is introduced into the second oil pump P via the pipe line 8 and the suction pipe 3, and the oil discharged from the second oil pump P is transferred to the ball-type reverse support valve 1 (delivery pipe). (Also called a delivery pipe or the like) to the hydraulic control circuit of the transmission.

  Next, the structure of the ball type reversely supported valve 1 will be described with reference to FIG. FIG. 2 is an enlarged cross-sectional view showing a ball-type reverse support valve included in the transmission hydraulic pressure supply apparatus shown in FIG.

  As shown in FIG. 2, the ball-type counter-support valve 1 in the present embodiment is also accommodated in a mounting hole Ta formed in the transmission case T and a mounting hole 6 a formed in the oil pump base 6 as in the conventional case. That is, the ball-type counter-support valve 1 is accommodated in a space formed by the attachment hole Ta and the attachment hole 6a by combining the transmission case T and the oil pump base 6. Further, by being accommodated, the transmission case T and the oil pump base 6 can be arranged in a state of straddling the mating surface X where the opposing end portions contact each other. In other words, the shape of the ball-type counter-support valve 1 (specifically, the cylindrical length from one open end to the other open end), the mounting holes for the transmission case T and the oil pump base 6 so as to be so Ta and 6a are formed.

  The ball-type counter-support valve 1 is formed in a cylindrical pipe shape having both ends opened with a step 9 in the outer shape, and the large-diameter portion 1 a and the small-diameter portion 1 b are connected by the step 9. ing. In order to receive the ball-type counter-support valve 1 having such a step 9, the mounting hole Ta on the transmission case T side is formed with a larger diameter than the mounting hole 6a on the oil pump base 6 side. The reason why the step 9 is formed in the ball-type reversely supported valve 1 is that the operation direction as the reversely supported valve by the valve seat 10 and the ball B inside the cylinder is limited to one direction. Further, a stopper pin S can be press-fitted into the ball-type counter-support valve 1, and the ball B that can move in the left-right direction in FIG. The stroke amount from the seat 10 to the first oil pump side is limited.

  A plurality of O-rings are arranged on the outer periphery of the ball-type counter-support valve 1. As can be understood from FIG. 2, in the present embodiment, at least one O-ring 2 b is disposed on the side closer to the second oil pump with the mating surface X as a base point, as in the conventional case, whereas the mating surface is different from the conventional one. The structure is such that at least one O-ring Ra is arranged on the front side of the stopper pin S with X as a base point. That is, in the past, the O-ring 2a was disposed outside the stopper pin S, that is, closer to the end portion with the mating surface X as a base point (see FIG. 3). The arrangement position of 2a and the stopper pin S is switched, and the O-ring Ra is arranged between the mating surface X and the stopper pin S. In other words, a ball-type reverse having a structure in which the stopper pin S can be press-fitted into a predetermined position nearer to the first oil pump than the plurality of O-rings 2b and Ra arranged on the outer peripheral portion. This is a branch valve 1.

As described above, in the ball type reversely supported valve 1 shown in the present embodiment, the press-fitting position of the stopper pin S and the arrangement position of the O-ring on the side close to the first oil pump are interchanged with each other, and the mating surface X is changed. As a base point, the front side of the stopper pin S is set as a new O-ring Ra arrangement position. That is, the stopper pin S can be arranged so as to include at least one of the plurality of O-rings 2b and Ra between the transmission case T and the mating surface X of the oil pump base 6. By doing so, even if the oil flowing in the ball-type counter-support valve 1 leaks through the stopper pin S, the transmission case T and the oil pump base 6 that accommodates the ball-type counter-support valve 1 through the mating surface X It will be possible to prevent leakage outside the case. Further, oil leakage to the suction pipe 3 side accommodated in the case via the mating surface X can also be prevented.
Therefore, it is not necessary to arrange the O-ring 2c on the mating surface X of the transmission case T and the oil pump base 6 so as to surround the ball-type counter-support valve 1 and the suction pipe 3 on the inner side, which reduces the number of parts. In addition, it is shown that it is not necessary to perform processing for arranging the O-ring 2c so as not to leak oil on at least one of the transmission case T and the oil pump base 6, and that oil leakage prevention can be achieved without cost. It is advantageous.

  As mentioned above, although an example of embodiment was demonstrated based on drawing, it cannot be overemphasized that this invention is not limited to this but various embodiment is possible. For example, in the above-described embodiment, an example in which only one second pump assembly 5 driven by the electric motor 7 is provided is shown. However, the present invention is not limited thereto, and a plurality of second pump assemblies 5 may be provided. Good. In this case, there is an advantage that even if one second pump assembly 5 breaks down, it can be immediately switched to another second pump assembly 5 for use.

DESCRIPTION OF SYMBOLS 1 ... Ball-type reverse support valve 2a-2c (Ra) ... O-ring (seal ring)
DESCRIPTION OF SYMBOLS 3 ... Suction pipe 4 ... Strainer 5 ... 2nd oil pump assembly 6 ... Oil pump base 6a, 6b ... Mounting hole 7 ... Electric motor 8 ... Pipe 9 ... Step 10 ... Valve seat A ... Press-fit part P ... 2nd oil pump S ... Stopper pin press-fitting portion T ... Transmission case Ta, Tb ... Mounting hole X ... Matching surface (boundary surface)

Claims (2)

A first oil pump driven by the main shaft of the transmission;
At least one second oil pump driven by suitable means;
An attachment member for attaching the second oil pump to the transmission case so as to be removable from the outside of the transmission;
A cylindrical ball-type reverse provided between the discharge side of the first oil pump and the discharge side of the second oil pump to block the flow of oil from the first oil pump to the second oil pump. The ball-type counter-support valve is provided in a space formed by combining a transmission case and the mounting member, and a discharge side of the first oil pump is connected to a hydraulic control device. In the transmission hydraulic supply device,
A plurality of sealing rings in the ball type check valve the outer periphery, it has inside the ball for blocking the flow of oil respectively, and mating surface between the transmission case and the mounting member, the stroke amount of the ball A transmission hydraulic pressure supply device arranged to include at least one of the plurality of seal rings between a stopper pin for limiting .   2. The hydraulic pressure supply device for a transmission according to claim 1, wherein the ball-type counter-support valve has the stopper pin disposed closer to the end than the seal ring of any of the plurality of seal rings.

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